CN210829251U - High-bearing coal mining machine traveling system - Google Patents
High-bearing coal mining machine traveling system Download PDFInfo
- Publication number
- CN210829251U CN210829251U CN201921977382.8U CN201921977382U CN210829251U CN 210829251 U CN210829251 U CN 210829251U CN 201921977382 U CN201921977382 U CN 201921977382U CN 210829251 U CN210829251 U CN 210829251U
- Authority
- CN
- China
- Prior art keywords
- tooth
- teeth
- traveling system
- cogwheel
- socket
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Gears, Cams (AREA)
Abstract
The utility model relates to a high bearing coal-winning machine traveling system, walking wheel and round pin row including direction piston shoes and intermeshing, the walking wheel is equipped with the double teeth of a cogwheel, and the structural parameter of the double teeth of a cogwheel is the same, the round pin is arranged and is equipped with double tooth's socket, and the structural parameter of double tooth's socket is the same, the teeth of a cogwheel corresponds the meshing with the tooth's socket according to arranging, the flank of tooth of the teeth of a cogwheel is the evagination surface on the tooth width direction, correspondingly, the cell wall of tooth's socket is interior concave surface on the tooth width direction, the walking wheel all is the state of mutual unsmooth gomphosis with round pin. The utility model discloses bearing capacity is big, and the reliability is high, can adapt to round pin drainage level bending, and walking wheel gear edge can not produce stress concentration, can adapt to the needs of coal-winning machine to adopting height, high-power direction development greatly better.
Description
Technical Field
The utility model relates to a coal-winning machine traveling system has higher bearing capacity, belongs to coal mining equipment technical field.
Background
The driving force for the coal mining machine to walk on the coal face in the underground coal mine is usually finally the meshing transmission of pin teeth of pin row series from the walking wheel of the coal mining machine and the scraper conveyor. The scraper pin row series consists of a plurality of pin rows with the same structure. The walking wheels and the scraper pin rows are in open non-conjugate engagement to drive the coal mining machine to walk back and forth in a traction manner. In the walking process of the working face, the pin row is allowed to deflect by 1 degree in the horizontal plane, and the pin row is used for meeting the requirements of the working face when the working face is pushed, rolled and straightened and a coal cutter walks an S-shaped cutting machine nest.
At present, the coal mining machine is developed towards the direction of large mining height and high power, the installed power of the coal mining machine reaches about 3000kW at most at home and abroad, the fully-mechanized mining height reaches more than 8m, and the total weight of the coal mining machine reaches more than 200 t. When the coal mining machine cuts coal, the working resistance is large, the working surface has an inclination angle, and the traction force of the coal mining machine needs to be increased, so that the traveling system of the coal mining machine faces the following two key problems:
1. how to improve the bearing capacity of a heavy large-modulus gear (modulus m is more than 46) and a pin row and avoid the stress concentration of the edge of the gear so as to increase the traction force output by a terminal traveling system of a coal mining machine and improve the reliability of the traveling system;
2. under the condition of large traction force of the coal mining machine, the contact stress between the travelling wheels and the pin rows is increased sharply. Under the condition that the pin row is horizontally bent, how to improve the meshing stress condition of the walking wheel teeth and the pin row and improve the reliability of a walking system.
Chinese patent application No. 200910044922.1 discloses a double-row driving chainless traction system for coal mining machine, which utilizes a plurality of pin rails arranged side by side and special traveling wheels (multi-row traveling wheels) engaged with the plurality of pin rails, wherein the gear teeth of each row of traveling wheels are engaged with the corresponding pin rails and the gear teeth of the other row of traveling wheels are engaged with the corresponding pin rails by a phase angle, the output force of each gear tooth is the same, the total traction force is greatly improved, and if the total traction force is not changed, the output force of each gear tooth is small, thereby improving the reliability of the equipment. The application does not solve the problem of how the walking wheel adapts to the horizontal deflection angle of the pin rail, does not solve the problem of tooth shape, and only increases the number of pairs of the teeth of the walking wheel meshed with the pin rail; in addition, because the tooth form of one row of pin rails is over against the tooth grooves of the other row, the pin rows are difficult to produce and manufacture in a segmented mode.
SUMMERY OF THE UTILITY MODEL
In order to solve the problem, the utility model provides a high coal-winning machine traveling system that bears, bearing capacity is big, and the reliability is high, can adapt to round pin drainage level bending, and walking wheel gear edge can not produce stress concentration, can adapt to the coal-winning machine to the needs of adopting high, the high-power direction development greatly better.
The utility model discloses a main technical scheme has:
the utility model provides a high bearing coal-winning machine traveling system, includes intermeshing's walking wheel and round pin row, the walking wheel is equipped with double teeth of a cogwheel, and the structural parameter of double teeth of a cogwheel is the same, the phase place is unanimous, and the both sides flank of every teeth of a cogwheel evaginates and the symmetry in the tooth thickness direction, the round pin row is equipped with double tooth's socket, and the structural parameter of double tooth's socket is the same, the phase place is unanimous, and both sides cell wall indent and symmetry in the tooth thickness direction of the teeth of a cogwheel with it meshing, the teeth of a cogwheel corresponds the meshing with the tooth's socket according to arranging, the flank of a cogwheel is evagination surface on the tooth width direction, correspondingly, the cell wall of tooth's socket is interior concave surface on the tooth width direction.
The walking wheels adopt straight gears, and the single-row gear teeth and the tooth grooves which are meshed with each other are symmetrical in the respective tooth width direction.
The profile of the tooth surface of the gear tooth on the normal section of each meshing position is in an outward convex shape, the profile can be an outward convex curve, or the middle section of the profile is a straight line, and the two side sections are circular arcs.
When the contour is a convex curve, the curve may be a segment of a circle or an ellipse.
Preferably, the curved line is an arc, the radii of the arcs corresponding to the profiles of the tooth surfaces of the gear teeth on the normal cross sections of the meshing positions are all equal and are recorded as R1, the profiles of the groove walls of the tooth grooves on the normal cross sections of the meshing positions are all concave arcs, the radii of the arcs are all equal and are recorded as R2, and R1 is less than R2.
The ratio of R1 to R2 is preferably between 0.85 and 0.98.
A pair of tooth sockets with the same phase are communicated, and a step is formed between the groove walls on the same side of the corresponding pair of tooth sockets at the communication position.
The utility model has the advantages that:
the utility model discloses an adopt neotype walking wheel and round pin row meshing structure, can be under the condition that does not change the walking wheel modulus, improve traveling system's bearing capacity, avoid the edge effect of the teeth of a cogwheel, avoid the teeth of a cogwheel unbalance loading edge stress to proliferate and collapse tooth or too early fatigue inefficacy, make coal-winning machine traction force output can continue the increase, perhaps under the condition of increase walking wheel modulus, improve the bearing capacity that the round pin was arranged, consequently, can satisfy the requirement of the big traction force of coal-winning machine heavy load, can improve traveling system's reliability again. Especially, the effect is more obvious under the condition of heavy-load traction of the coal mining machine.
The utility model discloses can adapt to the orbital horizontal bending of walking well, when the working face pushed away the swift current not straight or the working face had the undulation, also perhaps when adopting the quick-witted nest to walk the S curved, the walking wheel was arranged with the round pin has automatic guiding to slow down the trend that the round pin was arranged and the walking wheel off-normal load meshing, consequently can improve the engaged state voluntarily to improve traveling system' S life-span.
Drawings
Fig. 1 is a schematic structural view of a meshing state of a walking wheel and a pin row according to an embodiment of the present invention;
FIG. 2 is a cross-sectional view C-C of FIG. 1;
FIG. 3 is a schematic structural view of a gear tooth of one embodiment of the road wheel;
FIG. 4 is a schematic view of a tooth slot profile of one embodiment of the pin row;
FIG. 5 is a schematic cross-sectional view of a slot wall of one tooth slot of the pin row;
fig. 6 is a schematic view of analysis of engagement stress of the traveling wheels and the pin rows when the two adjacent pin rows have an intersection angle.
Detailed Description
The utility model discloses a high coal-winning machine traveling system that bears (for short traveling system), as shown in fig. 1-6, including intermeshing's walking wheel 1 and round pin row 2, the round pin is arranged and is fixed on scraping the trigger along working face length direction, and the walking wheel is arranged two-way meshing along the round pin, drives the reciprocal walking of coal-winning machine along the working face. The traveling wheels are provided with double rows of gear teeth 11 and 12, the double rows of gear teeth are machined on the same gear blank, the structural parameters of the double rows of gear teeth, such as the number of teeth, the modulus, the diameter of a tooth top circle, the shape of a tooth profile line and the like, are the same, and the phases are consistent. The two side tooth surfaces of each gear tooth are convex and symmetrical in the tooth thickness direction. The pin row is provided with double rows of tooth grooves, and the structural parameters of the double rows of tooth grooves are the same and the phases are consistent. The gear teeth are correspondingly meshed with the tooth grooves in rows. The two side walls of each tooth space (and also the tooth flanks of the teeth of the pin row) are concave (e.g., may be concave arcs) and symmetrical in the tooth thickness direction of the tooth teeth that mesh with it.
Through the meshing of double-wheel teeth, when the walking wheel is meshed with the pin row to walk, the walking wheel can bear larger traction force of the coal mining machine. If meet abnormal conditions, for example after a certain gear teeth breaks off, another parallel gear teeth participate in the meshing, can meet an urgent need and drive the coal-winning machine to produce along the working face, do not influence output, wait to change again when the maintenance shift and fall unusual walking wheel, consequently improved traveling system's reliability greatly.
The center distance of the double row of gear teeth 11 and 12 in the tooth width direction is D1, and is equal to the center distance D2 of the tooth spaces in pairs juxtaposed on the pin row in the tooth width direction.
The tooth surface of the gear tooth is an outer convex surface in the tooth width direction, namely the closer to two ends of the tooth width direction, the thinner the tooth thickness is, and the closer to the middle of the tooth width direction, the thicker the tooth thickness is. Accordingly, the groove wall of the tooth groove is an inner concave surface in the tooth width direction, that is, the tooth thickness of the teeth on the pin row is thicker as the teeth are closer to both ends in the tooth width direction, and the tooth thickness is thinner as the teeth are closer to the middle in the tooth width direction. The walking wheel and the pin row are in a mutual concave-convex embedded state on the normal section of each meshing position of any gear tooth profile curve.
The gear is a straight gear. The single row of engaged teeth and tooth spaces are preferably symmetrical in the respective tooth width directions, and in an ideal engagement state, the theoretical contact point of the tooth and tooth space is located on the symmetrical center plane of the corresponding tooth space in the tooth width direction.
The normal cross-section extends along a normal to the tooth flanks of the engagement position. Each engagement location corresponds to a normal cross-section. Taking the walking wheel as an example, each point on the tooth profile curve of the gear tooth corresponds to a meshing position, namely a normal section, the common normal line passing through the meshing position is positioned in the corresponding normal section, and the normal section is parallel to the axis of the walking wheel.
Further, the tooth surface of the gear tooth has an outward convex profile on the normal section of each meshing position, and the profile can be in a convex curve shape or a composite shape with a straight middle section and circular arc sections at two sides.
When the contour is a convex curve, the curve may be a circular arc or a segment of a curve on an ellipse.
In the embodiment shown in the drawings, the curves preferably adopt circular arcs, and the radii of the circular arcs corresponding to the profiles of the tooth surfaces of the gear teeth on the normal cross sections of the various meshing positions are all equal and are denoted as R1, where the equal radii of the circular arcs mean that the radii of the circular arcs of two tooth surface contour lines of the same gear tooth on the same normal cross section are equal, and the radii of the circular arcs of the tooth surface contour lines on the normal cross sections of different meshing positions of the same gear tooth are also equal. Correspondingly, the contour of the groove wall of the tooth groove on the normal section of each meshing position is an inward concave circular arc, and the radiuses of the circular arcs are equal and are recorded as R2. The same meaning of the radii of the arcs on the tooth grooves is the same as that of the teeth.
Preferably, R1< R2 can eliminate or obviously reduce the edge effect of the gear teeth under heavy load when the travelling wheels are meshed with the pin row, and is beneficial to avoiding or reducing the gear teeth from being cracked or prematurely fatigue failure due to the sharp increase of the eccentric load edge stress of the gear teeth. Moreover, in the meshing process, due to the elastic deformation of the gear teeth, the tooth surface of the gear teeth of the walking wheel gear and the tooth surface of the pin row teeth can form curve line contact, so that the contact stress is obviously reduced, the bearing capacity is improved, and the wear resistance and the service life are obviously improved.
As a further preferable technical scheme, the ratio of R1 to R2 is controlled to be 0.85-0.98, so that on one hand, the edge effect of a traveling wheel of a coal mining machine under a heavy load condition is avoided, the phenomenon that the edge of the traveling wheel tooth in the tooth width direction is subjected to stress concentration to crack is prevented, and on the other hand, the tooth can keep high strength.
As shown in fig. 4 and 5, a pair of tooth grooves of the same phase are communicated with each other, and a step 22 is formed between the groove walls 21 and 23 of the corresponding pair of tooth grooves. The so-called step is relative to the inner concave surface of the groove walls 21 and 23, so that the communication is significantly narrowed compared to the tooth grooves. The surface shape of the step 22 is not particularly limited, but the side line of the step 22 in the normal section of each engagement position is preferably linear, and the structure is simple and easy to process.
As shown in fig. 5, when the output force of the road wheel is increased, if the section of the tooth profile of the pin row along the tooth width direction is a large arc, the sectional area of the tooth profile is greatly reduced compared with the structure shown in fig. 4, such as the area of the shaded part in fig. 5, so that the strength of the tooth profile of the pin row is greatly weakened, the reliability of the pin row is reduced, and the pin row is broken in severe cases. The utility model discloses an adopt the double tooth's socket that figure 4 is shown to be linked together the structure with the notch of narrowing between the tooth's socket in pairs, can prevent that the round pin from arranging the middle part fracture in the tooth width direction, improved the round pin and arranged serrated bearing capacity.
When the walking wheels and the pin rows are meshed to walk, the S-shaped curve is formed by the mining machine pit, or when the coal mining machine walks on a straight line section but the working surface is pushed to be uneven or the working surface fluctuates, an included angle α (shown in figure 6) is often formed between every two adjacent pin rows, although the theoretical contact point of the tooth grooves of the walking wheels and the pin rows deviates from the symmetrical central plane of the tooth grooves in the tooth width direction, the tooth grooves and the pin rows can still keep circular arc curves meshed, the situation that the tooth surfaces are cracked due to the fact that the stress of the tooth teeth of the traditional cylindrical gear is greatly increased due to the meshing of edge contact points cannot occur, meanwhile, the meshing force F between the walking wheels and the pin rows can be decomposed into mutually vertical component forces Fn and Ft, as shown in figure 6, the meshing component Fn has the tendency that the walking wheels are pushed to enable the contact points of the tooth grooves and the tooth grooves to move towards the symmetrical central plane in the tooth width direction, therefore, the meshing state can be spontaneously improved, the walking system can be well applicable to the walking system, and the novel walking system has the practical and the practical walking system can be well adapted to the practical use of the coal mining machine.
The walking wheel can adopt big modulus walking wheel, owing to adopt the utility model discloses an engagement structure, corresponding coal-winning machine traveling system can satisfy the needs of adopting height, high-power occasion to big traction force greatly, can also keep higher reliability and to walking orbit horizontal bending's adaptability simultaneously.
Claims (10)
1. The utility model provides a high coal-winning machine traveling system that bears, includes intermeshing's walking wheel and round pin row, its characterized in that: the walking wheel is equipped with double teeth of a cogwheel, and the structural parameter of double teeth of a cogwheel is the same, the phase place is unanimous, and evagination and symmetry are gone up to the both sides flank of every teeth of a cogwheel in the tooth thickness direction, the round pin is arranged and is equipped with double tooth's socket, and the structural parameter of double tooth's socket is the same, the phase place is unanimous, and indent and symmetry are gone up in the tooth thickness direction of the teeth of a cogwheel of every tooth's socket meshing with it to the both sides cell wall of every tooth's socket, the teeth of a cogwheel corresponds the meshing with the tooth's socket according to arranging, the flank of a cogwheel is evagination surface on the tooth width direction, correspondingly, the cell wall.
2. The high-capacity shearer loader traveling system according to claim 1, wherein: the walking wheels adopt straight gears, and the single-row gear teeth and the tooth grooves which are meshed with each other are symmetrical in the respective tooth width direction.
3. The high-capacity shearer loader traveling system according to claim 2, wherein: the tooth surface of the gear tooth is in an outward convex shape on the normal section of each meshing position, the outline is an outward convex curve, or the middle section of the outline is a straight line, and the two side sections are circular arcs.
4. The high-capacity shearer loader traveling system according to claim 3, wherein: when the contour is an outward convex curve, the curve is a section of curve on an arc or an ellipse.
5. The high-capacity shearer loader traveling system according to claim 4, wherein: the curve is an arc, the radii of arcs corresponding to the profiles of the tooth surfaces of the gear teeth on the normal cross sections of the meshing positions are equal and are recorded as R1, the profiles of the groove walls of the tooth grooves on the normal cross sections of the meshing positions are all concave arcs, the radii of the arcs are equal and are recorded as R2, and R1 is less than R2.
6. The high-capacity shearer loader traveling system according to claim 5, wherein: the ratio of R1 to R2 is between 0.85 and 0.98.
7. The high haulage shearer loader traveling system according to claim 1, 2, 3, 4, 5, or 6, wherein: a pair of tooth sockets with the same phase are communicated, and a step is formed between the groove walls on the same side of the corresponding pair of tooth sockets at the communication position.
8. The high-capacity shearer loader traveling system according to claim 7, wherein: the pin row is provided with a plurality of sections which are sequentially arranged along the length direction of the working face to form a track of the walking wheels.
9. The high-capacity shearer loader traveling system according to claim 7, wherein: 4-8 tooth grooves are arranged on the single-section pin row in a single row.
10. The high-capacity shearer loader traveling system according to claim 7, wherein: the walking wheels are large-module walking wheels.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921977382.8U CN210829251U (en) | 2019-11-15 | 2019-11-15 | High-bearing coal mining machine traveling system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921977382.8U CN210829251U (en) | 2019-11-15 | 2019-11-15 | High-bearing coal mining machine traveling system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210829251U true CN210829251U (en) | 2020-06-23 |
Family
ID=71264456
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921977382.8U Active CN210829251U (en) | 2019-11-15 | 2019-11-15 | High-bearing coal mining machine traveling system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210829251U (en) |
-
2019
- 2019-11-15 CN CN201921977382.8U patent/CN210829251U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8793969B2 (en) | Round steel chain | |
| AU2006203553A1 (en) | Chain drive or return arrangement and chain assembly and sprocket employed therein | |
| US20120094795A1 (en) | V-shaped transmission belt and belt wheel and method of use | |
| GB2127127A (en) | Drive chain | |
| EP2385923B1 (en) | Link chain for chain conveyors and horizontal chain links therefor | |
| JP2009526176A (en) | A kind of gear pair for power transmission in a speed accelerator and a speed reducer and method of forming the same | |
| MX2008011897A (en) | Link chain for chain conveyors and chain wheel therefor. | |
| CN210829251U (en) | High-bearing coal mining machine traveling system | |
| CN110644989A (en) | High-bearing coal mining machine traveling system | |
| CN203009697U (en) | Double-pitch variable-pitch silent chain | |
| AU2010274691A1 (en) | Rack and pinion arrangement for a mining extraction machine and rack and pinion rod therefor | |
| CN209369804U (en) | It is adapted to the Mars Miner single-wheel running gear of high abrasion easily accumulation mineral aggregate | |
| CN115769001A (en) | Drive for a rolling mill drive, rolling mill drive having a drive and use of a drive as a rolling mill drive | |
| CN203309008U (en) | Novel Hy-Vo tooth-shaped chain | |
| US4850648A (en) | Gear rack for driving or guiding a drum cutter loader | |
| CN109505596A (en) | It is adapted to the Mars Miner single-wheel running gear of high abrasion easily accumulation mineral aggregate | |
| CN102575518B (en) | Feed system for an underground winning machine, rack bar and drive sprocket therefor | |
| CN2937027Y (en) | Universal pin line | |
| CN201521597U (en) | Mute chain | |
| US4819989A (en) | Propulsion systems for mineral mining machines | |
| CN108678742B (en) | Height-adjustable multi-output coal mining machine travelling mechanism | |
| CN211008634U (en) | Short-machine-face alternating-current traction coal mining machine with ultra-thin coal seam and short machine body | |
| CN203925492U (en) | Thin and medium-thickness seam high bearing capacity walking wheel of coal cutter | |
| CN2592871Y (en) | Integral die-forged pin-rail | |
| CN204110792U (en) | Mine traction type self adaptation belt feeder pin tooth transmission trailer coupling |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |