CN107416052B - Tracked vehicle supporting mechanism and tracked vehicle - Google Patents

Abstract

The invention relates to a crawler support mechanism and a crawler, wherein the crawler support mechanism comprises a balance beam and a support rolling assembly, the base end of the balance beam, which is positioned in the middle, is hinged on a crawler frame of the crawler, the two sides of the balance beam are provided with support ends, the support rolling assembly is respectively hinged on the support ends of the balance beam and can move up and down through the swinging of the balance beam, and the support rolling assembly comprises a support crawler and a roller ring chain, and the roller ring chain is wound on the support crawler and is pressed on a crawler rail below the support crawler. The crawler support mechanism has a load distribution function, even if the crawler vehicle runs on an uneven road, each support can always tightly press each roller below the crawler vehicle on the crawler track below the crawler vehicle, and the crawler vehicle swings up and down along with the fluctuation of the terrain, does not derail, and can prolong the service life of the crawler.

Description

Tracked vehicle supporting mechanism and tracked vehicle

Technical Field

The invention relates to a crawler support mechanism, and belongs to the technical field of crawler travelling mechanisms.

Background

The domestic wind power market is rapidly developed in recent years, wind energy resources in plain areas with good construction conditions are almost completely developed, wind energy developed at present is gradually transferred to mountain areas and seas with difficult construction conditions, and accordingly, the rise of water and the rise of construction cost are caused, so that how to control investment cost becomes an important work of each construction unit. The road construction cost of the wind farm is taken as an important component of the construction engineering investment of the wind farm in mountainous areas, and naturally becomes an object for the thousand-square hundred-meter control of the construction party.

As a design party, how to design a road can ensure the transportation safety of equipment, and the engineering quantity is minimized, thereby becoming the primary purpose of the design party. The road construction of the mountain wind power plant is an indispensable link of the wind power plant construction, and because the road construction in the wind power plant is influenced by the wind power of the mountain and the mountain potential, the road line selection mode and method are focused on the construction aspect, and meanwhile, the details and the key points in the road design and the construction process are considered in detail so as to save the construction cost and protect the environmental resources. In addition to the width and longitudinal gradient of the road, the widening of the turning section is also an important influencing factor for the amount of road work, which has to take into account the length of the equipment vehicle and its mode of transportation.

Because the axle distance of the special vehicle specially designed for transporting wind power equipment is larger, the widening value of the turning section road is larger, the climbing capacity of the wheeled vehicle is weaker, and traction of other vehicles is often required when the wheel vehicle climbs a steep slope with larger gradient. However, in theory, tracked vehicles are preferred over wheeled vehicles in both respects.

However, existing tracked vehicles, tanks and armored vehicles pursue speed and vibration damping effects and other off-road properties, the thrust wheels of which are independently suspended, and the working stroke of which relative to the vehicle body moves up and down is very large. If a special vehicle for transporting the wind power equipment is designed by imitating a supporting mechanism of a tank or an armored carrier, a hanging mechanism of the special vehicle is extremely huge due to the fact that a tower barrel and a cabin of the wind power equipment are too heavy, and the cost is high; in addition, the heavy load during transportation and the light load during return are quite different, and the vibration reduction effect is poor.

In a typical track-mounted vehicle such as a crawler excavator, a bulldozer, a tractor, a carrier vehicle, and a pile driver, the thrust wheels are not independently suspended, but are fixed below linear rigid track frames (or track beams) on both sides of a frame and integrated with the frame, and the thrust wheels cannot move up and down relative to the track frames, are in direct contact with a grounded track rail, and roll on the track rail. In the structural form, the gravity of the vehicle and the gravity of the vehicle carried objects are transmitted to the thrust wheels through the track frames on two sides of the vehicle frame through the thrust wheel shafts and the thrust wheel bearings, and then transmitted to the track caterpillar tracks contacted with the thrust wheels through the thrust wheels, and finally transmitted to the ground through the track shoe.

In the supporting mechanism in the structure, when the crawler carrier is used as a crawler carrier and runs on a rugged road with a harder pavement, the load born by each supporting wheel is extremely uneven, for example, when the vehicle runs on a lower concave pavement, the two sides of the vehicle only bear the gravity of the whole crawler carrier and the gravity of a vehicle knapsack, and the supporting wheel bearing rotates relative to the supporting wheel shaft under the condition of bearing the load; if the installation position of the driving wheel and the inducer installed on the track frame is low and the lower surface thereof is almost level with the thrust wheel, the driving wheel and the inducer bear load; when the vehicle runs on the upward convex road surface, only one or two supporting wheels in the middle of the crawler frame bear load on two sides of the vehicle. When the vehicle runs on an uneven road surface, two bearing wheels are arranged at two sides of the vehicle to bear load, so that the load is concentrated too, and the load of the stressed part is too large. In practical use, the contact stress of the thrust wheel and the caterpillar track is too large, and the thrust wheel bearing rotates relative to the thrust wheel shaft under the condition of bearing a large load, so that the thrust wheel, the caterpillar track and the thrust wheel bearing are easy to damage.

In addition, because the actual grounding pressure is not an average value but is a point-like concentrated force which cannot be determined at all because the actual grounding pressure is always in the condition that only the individual thrust wheels bear load, and when the vehicle is heavy in carrying, the concentrated force can easily press and bend the track shoe; when the track wheel turns on a rugged road, the track and the track wheel are transversely and seriously misplaced in the turning process or after the completion of the turning because a plurality of track wheels are suspended, and if the track wheel continues to run, the track-biting phenomenon can occur when the track wheel falls down, so that the service life of the track is seriously influenced.

That is, the existing track vehicle supporting mechanism is only suitable for track vehicles which have light dead weight and carrying objects, small ground contact pressure, very flat road surfaces or soft road surfaces and rarely run on roads to slowly run on the roads.

Therefore, developing a crawler carrier vehicle capable of carrying wind power, such as a tower, a cabin, blades and the like, on a relatively large-gradient and relatively hard road surface and running at a relatively high speed is a problem to be solved in the wind power transportation industry.

In recent years, although several manufacturers develop crawler vehicles specially for wind power transportation, and the crawler vehicles can be used as a transport vehicle, a tractor or a trailer, because the supporting mechanism of the crawler vehicles still adopts a traditional structural form, the running speed of the crawler vehicles is very low, when the vehicles run on a harder road surface, the vibration is very serious, and the service life of the crawler is very short.

There is no crawler transport vehicle capable of carrying large heavy objects to rapidly travel on uneven roads in the prior art. Therefore, the supporting mechanism of the tracked vehicle is developed, so that when the tracked vehicle runs on an uneven road, each supporting rolling assembly for supporting the dead weight and carrying weight of the vehicle body can swing up and down along with the fluctuation of the road surface, the load of each supporting end is automatically and uniformly distributed, the supporting rolling assembly is not derailed, the phenomenon of rail biting can not occur, and the supporting mechanism does not have a bearing which is like the prior device and is easy to damage due to relative rotation under the condition of bearing heavy load, thereby greatly improving the running speed of the tracked vehicle and the service life of the tracked vehicle, and becoming a key technical problem which is urgently needed to be solved by engineering technicians in the field.

Disclosure of Invention

The present invention has been made to solve the above problems, and an object of the present invention is to provide a crawler support mechanism and a crawler, in which when the crawler runs on an uneven road, each support rolling assembly supporting the weight of the vehicle body and the back weight can swing up and down along with the fluctuation of the road surface, the support rolling assembly is forced relatively uniformly, the support rolling assembly is always pressed on the track, the derailment and the "track biting" phenomenon do not occur, and the support mechanism has no easily damaged bearing which rotates relatively under the condition of bearing heavy load as in the conventional device, thereby greatly improving the running speed of the crawler and the service life of the crawler.

In order to achieve the above purpose, the invention adopts the following technical scheme: the utility model provides a crawler support mechanism, includes compensating beam and a heavy rolling assembly, the base end at middle part of compensating beam articulates on the track frame of crawler, and its both sides have a heavy end, a heavy rolling assembly articulates respectively and is in each heavy end of compensating beam, and through the swing of compensating beam can the up-and-down motion, a heavy rolling assembly includes a heavy track and running roller ring chain, and the running roller ring chain winds on the heavy track to press on the track caterpillar track of its below.

The supporting track is strip-shaped, a closed-loop track with a trapezoid cross section is arranged on the periphery, and the hinge supporting point is positioned in the middle of the length direction of the closed-loop track; the roller ring chain is formed by connecting two ends of a roller shaft of an adjacent roller unit through chain plates, the roller unit comprises rollers, the roller shaft and bearings, the rollers are cylindrical, flanges are arranged at two axial ends, and the bearings arranged at the two ends are supported on the roller shaft and can rotate; at least a portion of the closed loop track and track caterpillar track of the track is captured between the flanges of the roller.

The supporting rolling assembly comprises a supporting track and a supporting wheel axially supported below the supporting track.

The supporting rolling assembly is a supporting wheel.

A tracked vehicle is provided with the tracked vehicle supporting mechanism.

The beneficial effects of the invention are as follows: the track vehicle supporting mechanism of the invention has a load distribution function, so that even if the vehicle runs on an uneven road, each supporting track always presses each roller below the supporting track tightly on a track rail below the supporting track, and swings up and down along with fluctuation of the terrain, and the supporting track is not separated from the track rail in the up and down direction. Because the track on the track and the caterpillar track are clamped between the flanges at the two ends of the roller and cannot move towards two sides relatively, even if the transverse resistance from the ground is large during steering, the roller and the caterpillar track below each track cannot be laterally dislocated, and the roller cannot leave the caterpillar track, so that the phenomenon of rail biting of the existing caterpillar vehicle cannot occur, the contact stress of the roller and the caterpillar track is small, and the service life of the caterpillar track can be greatly prolonged.

Drawings

FIG. 1 is a front elevational view of the track vehicle mounting track vehicle support mechanism of the present invention;

FIG. 2 is a left side elevational view of the construction of the tracked vehicle-mounted tracked vehicle support mechanism of the present invention;

fig. 3 is a schematic frame construction of the tracked vehicle of the present invention, wherein: (a) is a front view, and (b) is a top view;

FIG. 4 is a front view, in longitudinal section, of a track vehicle weight-bearing mechanism;

fig. 5 is a cross-sectional left side view of a tracked vehicle support mechanism;

fig. 6 is a structural view of a balance beam of a track vehicle weight bearing mechanism, wherein: (a) is a front view, (b) is a left view, and (c) is a schematic structural diagram for analyzing the motion relationship of each hinge point on the balance beam;

fig. 7 is a track-to-track construction diagram of a track vehicle track-to-track mechanism, wherein: (a) is a front view, (b) is a left view, and (c) is a schematic diagram for analyzing the motion relationship of each point on the crawler;

FIG. 8 is a partial block diagram of a roller ring chain of a crawler support mechanism, wherein: (a) is a front view, (b) is a top view, and (c) is a cross-sectional view of the roller unit;

FIG. 9 is a schematic view of a track roller assembly with a roller ring chain wrapped around the outer circumference of the track, wherein: (a) is a front view, and (b) is a left view;

fig. 10 is a block diagram for analyzing the law of motion of a crawler support mechanism.

Detailed Description

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

As shown in fig. 1, 2, 3 (a) and 3 (b), the tracked vehicle of the present invention mainly comprises: an engine (not shown), a frame 7, a track frame 10 integrally provided on both sides of the frame 7 in the left-right direction (the left-right direction refers to the left-right direction as viewed in the vehicle forward direction, the same applies hereinafter), a driving wheel 20, an inducer 50, a carrier roller 12, a track 40, a tooling 13 mounted above the frame 7, and a tracked vehicle support mechanism 1 of the main structural feature of the present invention.

Two pin holes 11' for hinging the crawler support mechanism 1 are provided in the front-rear (the vehicle advancing direction is front and vice versa, the same below) direction of the crawler frame 10. The base end of the tracked vehicle supporting mechanism 1 is hinged on the track frame 10 through a balance beam base end pin 11. The crawler frames 10 are arranged one in front of and behind each other, so that 4 crawler vehicle supporting mechanisms 1 of the invention are arranged on both sides.

As shown in fig. 4, 5, 6 (a) and 6 (b), the crawler support mechanism 1 comprises a balance beam 60 and a support rolling assembly 90, wherein a base end 60-1 of the balance beam 60 positioned in the middle is hinged on a crawler frame 10 of the crawler, two sides of the support rolling assembly are provided with support ends 60-2, and the support rolling assembly 90 is hinged on each support end 60-2 of the balance beam 60 and can move up and down through the swinging of the balance beam 60; the distance A from the support weight end 60-2 to the base end 60-1 on both sides of the balance beam 60 is equal; the support rolling assembly 90 comprises a support track 70 and a roller ring chain 80 wound on the support track 70; the hinge point of the support shoe 70 is positioned in the middle of the length direction of the support shoe 70; the roller ring chain 80 includes a roller 72, a roller shaft 73, and a link plate 71, the roller 72 is cylindrical, both axial ends have flanges 76, the link plate 71 is rotatably mounted on the roller shaft 73, both axial ends of the roller shaft 73 are fixed to the link plate 71, at least a part of the crawler belt 40 and the crawler belt 70 is caught between the flanges 76, and an axially inner surface 83 of the flange 76 is inclined outward.

The base end 60-1 of the balance beam 60 is provided with a balance beam hinge pin hole 11', the base end 60-1 of the balance beam 60 is hinged on the track frame 10 by a balance beam base end pin shaft 11, two support weight ends 60-2 below the balance beam 60 are also provided with support weight rolling assembly hinge holes 61' for hinging the support weight rolling assemblies 90, and the distances A from the two support weight rolling assembly hinge holes 61' to the balance beam hinge pin hole 11' are equal in the horizontal direction in front and behind the balance beam hinge pin hole 11'.

From theoretical mechanics statics knowledge, when the balance beam hinge pin hole 11 "of the base end 60-1 of the balance beam 60 is acted with the downward force W, if the distances a from the balance beam hinge pin hole 11" to the balance beam hinge pin hole 11 "are equal in the horizontal direction before and after the two support rolling assembly hinge holes 61' of the balance beam 60 support weight end 60-2, the forces F applied to the two support weight ends 60-2 are equal, and the balance beam 60 maintains the state shown in fig. 6 (a). However, if the upward forces applied to the hinge holes 61' of the two weight rolling assemblies of the two weight ends 60-2 are not equal, the balance beam 60 will swing about the balance beam base end pin 11.

As shown in fig. 6 (c), the triangle LMN moves in a plane and the point L can only move up and down, while the point N can only move horizontally, and when the point M moves up by the distance H, the triangle LMN moves to the position of the dotted triangle L ' M ' N '. From the geometry, h=h/2 if z=0, H < H/2 if z+.0.

This means that when the forces applied to the hinge holes 61' of the two weight rolling assemblies 60-2 of the balance beam 60 are unbalanced, the balance beam 60 swings around the hinge pin 11 of the base end of the balance beam, and if the height of the hinge hole 61' of one weight rolling assembly is kept constant, the height of the hinge pin 11 of the base end of the balance beam is less than half the height of the hinge hole 61' of the other weight rolling assembly.

As shown in fig. 7 (a) and 7 (b), the crawler belt 70 is long, the two ends are connected by smooth curve transition, the periphery is provided with a closed-loop track 68 with a ladder-shaped section, and inclined surfaces 69 on the two sides have a certain included angle.

As shown in fig. 7 (a), the crawler shoe 70 is further provided with a crawler shoe shaft 61 which is hinged to the crawler roll assembly hinge hole 61' of the balance beam 60 at the middle in the longitudinal direction thereof. I.e., a straight track under the track 70, the front and rear end points X, Y of which are equidistant from the track axis 61 in the horizontal direction B.

In this structure, the crawler belt 70 is swingable around the crawler belt shaft 61, and if a downward concentrated force T is applied to the crawler belt shaft 61, the upward crawler reaction force received by the crawler belt 70 is generally uniformly distributed as shown in fig. 7 (a). However, if the support reaction force below the support shoe 70 is not uniformly distributed, for example, if the support reaction force from the midpoint of the support shoe 70 to the front X point is large, the support shoe 70 swings in the clockwise direction about the support shoe shaft 61; conversely, if the support reaction force from the midpoint of the support shoe 70 to the rear Y point is large, the support shoe 70 swings counterclockwise about the support shoe shaft 61.

As shown in fig. 7 (c), if the point S representing the track shaft 61 is moved up and down only and the point Y is moved horizontally, the distance H '< H'/2 is moved upward when the point X is moved upward by the distance H ', from the point X to the point X', the point Y to the point Y ', and the point S to the point S', similarly to the movement law of the analysis balance beam 60.

This means that when the counter force of the support under the support shoe 70 is unbalanced, the support shoe 70 swings around the support shoe shaft 61, and if the height of one side (at the X or Y point) under the support shoe 70 is kept unchanged, the height of the support shoe shaft 61 raised (lowered) is less than half the height of the other side (at the Y or X point) raised (lowered).

As shown in fig. 8 (a), 8 (b), 8 (c), the roller ring chain 80 includes a roller unit 81 and a link plate 71. The roller unit 81 mainly comprises a roller 72, a roller shaft 73, a bearing 78, a sealing ring 79, an end cover 77 and a shaft end fixing push block 75. The roller 72 is supported on the roller shaft 73 by bearings 78 mounted at both ends and is axially fixed by an end cap 77, so that the roller 72 can rotate around the roller shaft 73. The two ends of the chain plate 71 are respectively provided with a hole, the aperture of the holes is equal to the shaft diameter of the chain plate 71 arranged at the two ends of the roller shaft 73, the two chain plates 71 are overlapped and fixed at the two ends of the roller shaft 73 by the shaft end fixing push block 75, and the chain plate 71 can rotate around the roller shaft 73; when the other end of the link plate 71 is connected to the roller shaft 73 of the adjacent roller units 81, a plurality of roller units 81 may be connected in a closed loop to form the roller ring chain 80. With this structure, the rollers 72 can flexibly rotate around the respective roller shafts 73, and the adjacent roller units 81 can rotate around the roller shafts 73 thereof. That is, such a roller chain 80 is flexible in its length direction, and may form a flexible closed loop.

As shown in fig. 8 (c), the roller 72 is formed in a cylindrical shape with a cylindrical surface 82 for bearing a load in the middle, and the axial length thereof is slightly longer than the width of the outer circumferential rail 68 on the crawler 70; annular flanges 76 are provided at both ends, and inner conical surfaces 83 are connected with cylindrical surfaces 82, so that the outward opening angle of the conical surfaces 83 at both sides is slightly larger than the included angle of inclined surfaces 69 at both sides of the peripheral track 68 of the crawler 70.

As shown in fig. 9 (a), 9 (b), when the roller ring chain 80 is looped around the outer circumference of the crawler 70, the groove formed by the conical surface 83 and the cylindrical surface 82 of the flanges 76 on both sides in the middle of the roller 72 can just be caught on the track 68 on the outer circumference of the crawler 70, and when the roller 72 rolls along the track 68 on the outer circumference of the crawler 70, the entire roller ring chain 80 can be circularly rotated around the crawler 70.

As shown in fig. 4 and 5, when the crawler support mechanism 1 of the present invention is hinged to the crawler frames 10 on both sides of the frame 7 by the balance beam base end pin 11, the grooves of the rollers 72 located below and encircling the support crawler 70 are just clamped to the track 41 of the ground engaging crawler 40. Since the support shoe 70 is supported by the roller 72 on the track 41 of the crawler belt 40, the support reaction force from the ground is transmitted directly from the track 41 of the crawler belt 40 to the support shoe 70 via the roller 72, and no bearing force is applied to the structure (the bearing 78 in the roller unit 81 receives the self weight of the roller 72 only when the link plate 71 lifts the roller 72 and returns it to the upper portion of the support shoe 70). The track 41 of the track 40 has a cross section substantially identical to the track 68 on the outer periphery of the track 70. During the track vehicle travel, the rollers 72 can roll along the track 41, while the track 70 moves linearly along the track 41.

As shown in fig. 4 and 5, if the road surface is flat, since the two weight rolling assembly hinge holes 61' are located in front of and behind the balance beam hinge pin hole 11″ in the horizontal direction and the distance a to the balance beam hinge pin hole 11″ is equal, the concentrated force transmitted from the track frame 10 to the balance beam 60 through the balance beam base end pin 11 is transmitted to the two weight shoes 70 hinged thereto through the weight shoe shaft 61, and the forces received by the two weight shoes 70 are equal. The support weight crawler shafts 61 are disposed in the middle of the support weight crawler 70 in the longitudinal direction, and the support weight crawler 70 can swing flexibly around the support weight crawler shafts 61, so that the support reaction forces from the rollers 72 borne by the two support weight crawler 70 are uniformly distributed in the longitudinal direction of the support weight crawler 70. That is, the forces applied to the track 41 of the track 40 by the two heavy shoes 70 through the rollers 72 are uniformly distributed. Therefore, it can be said that the weight of the vehicle itself and the weight of the vehicle carried by the vehicle can be uniformly transmitted to the track rail 41 of the crawler 40 in contact with the roller 72 via the balance beam 60, the weight bearing 70 and the roller 72 of the crawler support mechanism 1 of the present invention by the crawler frames 10 on both sides of the frame 7, and thus uniformly transmitted to the ground.

As shown in fig. 10, if the road surface is not flat, for example, there is a protrusion at the crawler belt 40 indicated by arrow D, so that the crawler belt 40 thereat is raised by a distance P, at this time, the roller 72 indicated by arrow E is still pressed against the caterpillar rail 41 of the crawler belt 40, the rear end of the counter weight crawler 70 is supported and rolls forward by a slight distance, and the counter weight crawler shaft 61 indicated by arrow K is lifted upward, and at the same time, the counter weight crawler 70 swings about the counter weight crawler base end pin 11, the rear counter weight crawler 70 is supported by the roller 72 below and moves forward by a slight distance, and the counter weight crawler base end pin 11 indicated by arrow C is lifted upward. As can be seen from the previous analysis, M < P/2, N < M/2, and therefore N < P/4. Since the balance beam base pin 11 is fixed to the track frame 10 of the frame 7, this means that the amplitude of the up-and-down fluctuation of the frame 7 is much smaller than the height of the road surface fluctuation, and the vibration is reduced, although the ground surface is uneven.

That is, the crawler support mechanism 1 of the present invention can uniformly distribute the load to the crawler tracks 41 therebelow, and the support tracks 70 and the balance beams 60 swing along with the up-and-down fluctuation of the terrain during the traveling of the vehicle, and the up-and-down vibration amplitude of the frame 7 is greatly reduced, which means that the crawler support mechanism 1 of the present invention has the load uniform distribution (distribution) and vibration reduction functions.

Since the crawler frame 10 on both sides of the vehicle is provided with the crawler support mechanism 1 of the present invention in front of and behind each crawler frame, each of the crawler 70 and the balance beam 60 can swing independently along with the up-and-down fluctuation of the terrain, and since the crawler 70 has a small length in the front-and-rear direction, the crawler 40 under it can be well attached to the ground, and the load borne by each track shoe is made substantially the same.

In addition, as shown in fig. 5, when the base end of the balance beam 60 of the crawler support mechanism 1 of the present invention is mounted on the crawler frame 10 of the frame 7 by the balance beam base end pin 11, the two fixing bushes 15 and 16 on the crawler frame 10 restrict the balance beam 60 from moving laterally in the axial direction relative to the crawler frame 10, so that the balance beam 60 can swing laterally together with the crawler frame 10 when the vehicle turns and the crawler frame 10 swings laterally. In addition, due to the limitation of the two split fixed sleeves 65, 66 on the balance beam 60, the track 70 cannot move laterally with respect to the balance beam 60, that is, the track 70 can swing laterally with the track frame 10 when the tracked vehicle turns.

Further, as shown in fig. 5, under the crawler 70, the rail 68 formed on the outer periphery of the crawler 70 is caught from above in the groove formed by the cylindrical surface 82 of the roller 72 and the conical surfaces 83 of the flanges 76 on both sides above the roller 72, and the track 41 of the crawler 40 is caught from below in the groove formed under the roller 72, so that when the crawler 70 moves laterally, the crawler 70 moves laterally together with the roller 72 and the track 41 of the crawler 40, thereby moving the crawler 40 laterally.

During this movement, the lateral force is transmitted from the fixed bush 15 or 16 of the crawler frame 10 to the balance beam 60, and then transmitted from the fixed bush 65 or 66 of the balance beam 60 to the crawler 70, and the tapered surface 83 of the flange 76 of the roller 72 in contact with the side surface of the lower rail 68 of the crawler 70 is pressed. The roller 72 receives a lateral force of the lateral movement, but the roller 72 does not turn sideways because the roller 72 receives a downward pressure from the crawler 70. Thus, the conical surface 83 of the other flange 76 on the roller 72 presses against the side surface of the track 41 in contact therewith, transmitting lateral force to the track 40, causing the track 40 to slide relative to the ground.

That is, the track vehicle supporting mechanism 1 of the present invention includes a balance beam 60 and a supporting rolling assembly 90, wherein a base end 60-1 of the balance beam 60 located at the middle is hinged on a track frame 10 of the track vehicle, both sides of the balance beam have supporting ends 60-2, and the supporting rolling assembly 90 is hinged on each supporting end 60-2 of the balance beam 60, respectively, and can move up and down by the swing of the balance beam 60; the track roller assembly 90 includes a track 70 and a roller link chain 80, with the roller link chain 80 wrapping around the track 70 and pressing against the track rail 41 therebelow. The support track 70 is long, a closed-loop track 68 with a trapezoid cross section is arranged on the periphery, and the hinge support point is positioned in the middle of the length direction; the roller ring chain 80 is formed by connecting two ends of roller shafts of adjacent roller units 81 through chain plates 71, wherein the roller units 81 comprise rollers 72, roller shafts 73 and bearings 78, the rollers 72 are cylindrical, flanges 76 are arranged at two axial ends, and the bearings 78 arranged at the two ends are supported on the roller shafts 73 and can rotate; at least a portion of the closed loop track 68 and the caterpillar track 41 of the track 70 are captured between the flanges 76 of the rollers 72.

Since the crawler vehicle weight bearing mechanism 1 of the present invention of this construction has a load distribution function, even when traveling on an uneven road, each weight bearing 70 always presses each roller 72 thereunder tightly against the crawler track 41 thereunder, and swings up and down with the relief of the terrain without disengaging from the track 41 in the up and down direction. Since the rails 68 on the counter-weight shoes 70 and the caterpillar tracks 41 of the caterpillar tracks 40 are clamped between the flanges 76 at the two ends of the rollers 72 and cannot move to the two sides relatively, even if the transverse resistance from the ground is large during steering, the rollers 72 and the caterpillar tracks 41 under each counter-weight shoe 70 cannot be laterally dislocated, and the rollers 72 cannot leave the caterpillar tracks 41, so that the phenomenon of rail biting like the conventional caterpillar vehicles cannot occur, the service life of the caterpillar tracks can be greatly prolonged, and the running speed of the caterpillar vehicles can be improved. In addition, since each roller 72 receives approximately the same load and the diameter of the roller 72 is large, the contact stress of the roller 72 with the caterpillar 41 is small, which is also an important factor for improving the life of the crawler belt.

The specific embodiments of the tracked vehicle supporting mechanism 1 according to the present invention have been described above, but in practice, a plurality of structural forms may be designed without departing from the core idea of the present invention.

For example, in the embodiment of the invention, the roller is made into a cylinder shape, and flanges are arranged at two ends, but the middle bulge can also be made into a shape that the section of the middle bulge is trapezoidal and the two ends of the middle bulge are cylindrical, and the track at the periphery of the corresponding support track and the caterpillar track are correspondingly changed.

In addition, the invention can directly arrange the thrust wheel at the weight end of the balance beam without arranging the weight track, thereby having a certain vibration reduction effect.

In addition, the invention can be provided with a supporting wheel below the supporting track instead of a roller ring chain, and the damping effect of the supporting wheel is equivalent to that of the embodiment of the invention, but the bearing of the supporting wheel is stressed.

The track vehicle supporting mechanism provided by the invention is described in detail above. The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present invention and its core ideas. It should be noted that it will be apparent to those skilled in the art that several improvements and modifications can be made to the present invention without departing from the principle of the invention, and these improvements and modifications are also within the scope of the claims of the invention.

Claims (2)

1. The utility model provides a crawler support mechanism, includes compensating beam and a heavy rolling assembly, the base end at middle part of compensating beam articulates on the track frame of crawler, and its both sides have a heavy end, a heavy rolling assembly articulates respectively each heavy end of compensating beam, and through the swing of compensating beam can the up-and-down motion, its characterized in that: the supporting rolling assembly comprises a supporting track and a roller ring chain, wherein the roller ring chain is wound on the supporting track and is pressed on a track caterpillar rail below the supporting track, the supporting track is long, a closed-loop track with a trapezoid cross section is arranged on the periphery of the supporting track, and the hinge supporting point is positioned in the middle of the length direction of the hinge supporting point; the roller ring chain is formed by connecting two ends of a roller shaft of an adjacent roller unit through chain plates, the roller unit comprises rollers, the roller shaft and bearings, the rollers are cylindrical, flanges are arranged at two axial ends, and the bearings arranged at the two ends are supported on the roller shaft and can rotate; the distance A from the support weight ends to the base ends of the two sides of the balance beam is equal, the support weight track is provided with a support weight track shaft hinged with the balance beam in the middle of the length direction of the support weight track, the linear track is arranged below the support weight track, and the distance B from the front end point X, Y and the rear end point X, Y of the track to the support weight track shaft is equal in the horizontal direction; the lower track of each supporting track is clamped in the grooves formed above the roller from above by the cylindrical surface of the roller and the conical surfaces of the flanges on the two sides, the track caterpillar is clamped in the grooves formed below the roller by the cylindrical surface of the roller and the conical surfaces of the flanges on the two sides from below, the supporting track runs on an uneven road, each roller below the supporting track is always tightly pressed on the track caterpillar below the supporting track, and the supporting track swings up and down along with fluctuation of the terrain, and is not separated from the caterpillar in the up and down direction.

2. A tracked vehicle, characterized in that: a tracked vehicle support mechanism having the tracked vehicle support mechanism of claim 1.

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