Movable type concrete mixing plant supporting facility dip angle aggregate batching machine

Abstract

The invention provides a movable concrete mixing plant supporting facility dip angle aggregate batching machine, and relates to the technical field of building construction machinery. The inclination angle aggregate batching machine of the supporting facility of the movable concrete mixing plant comprises a horizontal inclination angle belt conveyor, a plurality of sets of belt carrier rollers are arranged on the horizontal inclination angle belt conveyor, each belt carrier roller comprises an axis roller, a sleeve is fixedly arranged on each axis roller in a sleeving mode, a corrugated pipe is arranged outside each sleeve in a sleeving mode, and the axis rollers are connected with the corrugated pipes in a sleeving mode. The two ends of the corrugated pipe and the two ends of the sleeve are flexibly sealed, a shell is arranged on the outer side of the corrugated pipe, and the corrugated pipe and the sleeve are filled with high-viscosity silicone oil. A spiral channel with a variable cross section is arranged on the outer wall of the sleeve, silicone oil flows in the spiral channel to generate self-excited oscillation, the corrugated pipe is axially compressed to reduce the local sectional area of a flow channel, and the silicone oil generates violent turbulence when passing through a narrow part to increase viscous resistance, so that impact and vibration on the belt carrier roller are effectively absorbed.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of construction machinery, in particular to a mobile concrete mixing station supporting facility inclined aggregate batching machine. BACKGROUND

[0002] The large-inclination horizontal conveyor gradually becomes the mainstream conveying equipment in scenarios such as high-rise building and bridge construction, due to its advantages of small floor space occupation and large conveying height.

[0003] However, the vibration generated by the operation of the conveyor can weaken the friction between the concrete and the belt, causing the concrete in the inclined section to slide off, and the impact of the sliding concrete on the carrier roller can shorten the fatigue life of the carrier roller bearing, and frequent impact can cause the axis of the carrier roller set to deviate, resulting in transverse deviation of the conveying belt. SUMMARY

[0004] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, the present application provides a mobile concrete mixing station supporting facility inclined aggregate batching machine, which comprises a horizontal-inclination belt conveyor, a rack is arranged on the horizontal section of the horizontal-inclination belt conveyor, a plurality of aggregate storage bins are arranged on the rack, an aggregate measuring hopper is arranged at the bottom end of each aggregate storage bin, a plurality of belt carrier rollers are arranged on the horizontal-inclination belt conveyor, the belt carrier roller comprises a shaft roller rotatably connected to a support, a sleeve is fixedly arranged on the shaft roller, a bellows is arranged outside the sleeve, the bellows and the sleeve are gap-fitted, the two ends of the bellows and the sleeve are flexibly sealed, an outer shell is arranged outside the bellows, and the outer shell is fixedly arranged on the shaft roller; the bellows and the sleeve are filled with high-viscosity silicone oil; and the outer wall of the sleeve is provided with a variable-section spiral channel.

[0005] Preferably, the space between the sleeve and the bellows forms a fluid damping channel.

[0006] Preferably, the spiral channel is arranged with equal pitch and equal depth, and the spiral channel penetrates through the two ends of the sleeve in the axial direction.

[0007] Preferably, the width of the spiral channel is gradually changed.

[0008] Preferably, the bellows is made of a metal structure, and the bellows has a deformation ability.

[0009] Preferably, end caps are symmetrically arranged at the two ends of the bellows and the sleeve, and the end caps are sealingly and slidingly arranged on the shaft roller.

[0010] Preferably, a sealing ring is coaxially arranged inside the end cap, and the sealing ring sealingly abuts against the bellows and the sleeve.

[0011] Preferably, the sealing ring is internally hollow.

[0012] Preferably, the bellows is axially and radially deformed after the belt roller is impacted, and the size of the fluid damping channel is changed.

[0013] Preferably, the high-viscosity silicone oil flows in the fluid damping channel after the belt roller is impacted, and viscous damping is generated when the high-viscosity silicone oil flows along the spiral channel.

[0014] The beneficial effects of the present application are:

[0015] 1. The high-viscosity silicone oil flows in the variable cross-section spiral channel after being impacted, generates self-excited oscillation, effectively absorbs the impact and vibration of the belt roller, avoids shortening the service life of the belt roller, and suppresses the axial deviation of the belt roller;

[0016] 2. The variable cross-section design of the spiral channel increases the fluid flow rate and enhances the turbulent flow intensity when the high-viscosity silicone oil flows from the wide end to the narrow end, which enhances the viscous damping effect;

[0017] 3. The bellows and the sleeve are designed with flexible sealing at both ends, which seals the gap and does not interfere with the deformation of the bellows, and can force the silicone oil to flow in the closed channel formed between the inner wall of the bellows and the outer side of the sleeve;

[0018] 4. By using the design of the bellows, when the belt roller is impacted and vibrated, the bellows will be axially compressed, causing the compression deformation of the wave crest and the wave trough, and reducing the local cross-sectional area of the flow passage, which will increase the flow rate of the silicone oil, and the dramatic increase in flow rate will cause severe turbulent flow when the silicone oil passes through the narrow part, which will increase the viscous resistance; at the same time, the pressure difference between the upstream and downstream of the flow passage increases, which can form a transient damping force acting on the bellows, which can reduce the impact force density per unit time and further suppress the vibration of the belt roller.

[0019] Additional aspects and advantages of the application will be set forth in part in the following description, will become apparent to those skilled in the art from the following description, or will be learned from practicing the application. BRIEF DESCRIPTION OF DRAWINGS

[0020] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings needed to be used in the embodiments. It should be understood that the following drawings only show some embodiments of the present application, and therefore should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can also be obtained without creative labor.

[0021] Figure 1This is a side view of the overall structure of a mobile concrete mixing station supporting facility inclined aggregate batching machine according to an embodiment of the present application. Figure 1 ;

[0022] Figure 2 This is a top view of the overall structure of an inclined aggregate batching machine, ancillary facilities of a mobile concrete mixing station, according to an embodiment of the present application;

[0023] Figure 3 This is a side view of the overall structure of a mobile concrete mixing station supporting facility inclined aggregate batching machine according to an embodiment of the present application. Figure 2 ;

[0024] Figure 4 1 is a schematic diagram of a partial structure of a belt idler according to an embodiment of the present application;

[0025] Figure 5 is a cross-sectional view of a belt idler according to an embodiment of the present application;

[0026] Figure 6 1 is a schematic diagram of the internal structure of a belt idler according to an embodiment of the present application;

[0027] Figure 7 This is an exploded view of the partial structure of a belt idler according to an embodiment of the present application;

[0028] Figure 8 According to the embodiment of this application Figure 5 A is an enlarged schematic diagram;

[0029] Figure 9 is a schematic diagram of the position and structure of the fatigue suppression mechanism according to an embodiment of the present application;

[0030] Figure 10 According to the embodiment of this application Figure 9 A magnified schematic diagram of middle B;

[0031] Figure 11 is an exploded view of a local structure of a fatigue suppression mechanism according to an embodiment of the present application;

[0032] Figure 12 According to the embodiment of this application Figure 11 A magnified schematic diagram of middle C;

[0033] Figure 13 is a schematic diagram of a partial structure of a fatigue suppression mechanism according to an embodiment of the present application;

[0034] Figure 14 is a schematic diagram of the structure in the spiral channel according to an embodiment of the present application;

[0035] Figure 15 It is a structural exploded diagram of the sleeve and boss according to an embodiment of the present application.

[0036] Icons: 1. Horizontal inclination belt conveyor; 11. Frame; 12. Aggregate storage silo; 13. Aggregate measuring hopper; 2. Belt roller; 21. Axial roller; 22. Casing; 221. Spiral channel; 222. Boss; 223. Groove; 23. Bellows; 231. End cover; 232. Sealing ring; 233. Peak portion; 234. Valley portion; 24. Casing; 3. Fatigue suppression mechanism; 31. Buffer assembly; 311. Arc-shaped elastic beam; 312. Connecting pin; 32. Sliding assembly; 321. Sliding pin; 322. Inner limit ring; 323. Outer limit ring; 324. Elastic part; 325. Ball head; 33. Inner cylinder; 331. Sliding pin mounting hole; 34. Support ring; 341. Honeycomb hole. DETAILED DESCRIPTION

[0037] The technical solutions in the embodiments of the present application will be described below in conjunction with the drawings in the embodiments of the present application.

[0038] To make the purpose, technical solutions, and advantages of the embodiments of this application more clear, the technical solutions in the embodiments of this application will be clearly and completely described below in conjunction with the drawings in the embodiments of this application. Obviously, the described embodiments are part of the embodiments of this application, not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0039] Example 1, as Figures 1-3 As shown, according to an embodiment of the present application, a mobile concrete mixing station supporting facility inclined aggregate batching machine includes a horizontal inclined belt conveyor 1, and the horizontal section of the horizontal inclined belt conveyor 1 is provided with a frame 11, and multiple groups of aggregate storage bins 12 are provided on the frame 11, and an aggregate measuring hopper 13 is provided at the bottom of each group of aggregate storage bins 12.

[0040] It should be noted that, in the specific embodiment of the present application, the aggregate storage bin 12 is a steel structure composed of a support frame, a bin body, a partition and a panel. In order to improve productivity and ensure measurement accuracy, two discharge ports are opened at the bottom of the aggregate storage bin 12, and cylinder-driven curved doors are installed below. The two curved doors can be opened simultaneously to achieve rapid and accurate weighing of aggregates. Each bin of the aggregate storage bin 12 is an independent structure and can be separated and combined. Each Aggregate storage silo 12 are each provided with Aggregate measuring hopper 13, each aggregate measuring hopper 13 is weighed by three 2000Kg "Toledo" high-precision sensors, and sand and gravel are measured simultaneously by four aggregate measuring hoppers 13, with fast measuring speed and high accuracy.

[0041] like Figures 3-8As shown, the horizontal inclination belt conveyor 1 is provided with a plurality of groups of belt rollers 2, the belt roller 2 comprises an axis roller 21 rotationally connected to a support, a sleeve 22 is fixedly sleeved on the axis roller 21, a bellows 23 is sleeved outside the sleeve 22, the bellows 23 and the sleeve 22 are in clearance fit, the bellows 23 and the sleeve 22 are flexibly sealed at two ends, an outer shell 24 is arranged outside the bellows 23, and the outer shell 24 is fixedly sleeved on the axis roller 21.

[0042] It should be noted that in the specific embodiments of the present application, the bellows 23 and the sleeve 22 are filled with high-viscosity silicone oil.

[0043] It should be further noted that the gap between the bellows 23 and the sleeve 22 cannot be too large to cause the fluid to directly pass through, resulting in damping failure, and the gap cannot be too small to cause the bellows 23 to be unable to deform.

[0044] As shown in the figure, Figure 6 The outer wall of the sleeve 22 is provided with a variable cross-section spiral channel 221.

[0045] It can be understood that the space between the sleeve 22 and the bellows 23 constitutes a fluid damping channel.

[0046] Further, the spiral channel 221 is arranged with equal pitch and equal depth, and the spiral channel 221 penetrates through both ends of the sleeve 22 in the axial direction.

[0047] The width of the spiral channel 221 is gradually reduced from right to left. Figure 6

[0048] It should be noted that the bellows 23 in the embodiments of the present application adopts a metal structure, and the bellows 23 has a deformation capability. It can be understood that the outer shell 24 is affected by impact or vibration during the conveying process, and the bellows 23 can be axially compressed and deformed.

[0049] As shown in the figure, Figures 6-8 The two ends of the bellows 23 and the sleeve 22 are symmetrically provided with end covers 231, and the end covers 231 are sealingly sleeved on the axis roller 21.

[0050] Further, a sealing ring 232 is coaxially arranged inside the end cover 231, and the sealing ring 232 sealingly abuts against the bellows 23 and the sleeve 22.

[0051] Further, the sealing ring 232 is hollow inside, and the hollow sealing ring 232 can deform itself, that is, to seal the gap without interfering with the deformation of the bellows 23, and can force the silicone oil to flow through the closed channel formed between the inner wall of the bellows 23 and the outside of the sleeve 22.

[0052] ​It can be understood that the bellows 23 is axially and radially deformed after the belt roller 2 is impacted, and the size of the fluid damping channel is changed.

[0053] Further, the high-viscosity silicone oil flows in the fluid damping channel after the belt roller 2 is impacted, and generates viscous damping when flowing along the spiral channel 221.

[0054] The following describes how to suppress vibration of the mobile concrete mixing station supporting facility inclined aggregate batcher in use according to an embodiment of the present application with reference to the accompanying drawings:

[0055] During the conveying process, the self-vibration of the horizontal inclined belt conveyor 1 and the impact generated by the rolling of concrete from the inclined section will drive the high-viscosity silicone oil to flow along the sleeve 22 in the fluid damping channel between the bellows 23 and the sleeve 22. Figure 6 For example, as shown in the working condition, when the silicone oil flows from the right side to the left side, the cross-sectional width of the spiral channel 221 is designed to be tapered, which can significantly increase the fluid flow rate based on the Venturi effect. At this time, the spiral channel 221 not only guides the silicone oil to form forced vortex flow, but also induces fluid self-excited oscillation, thereby effectively absorbing vibration and impact energy.

[0056] At the same time, the bellows 23 is axially compressed after being stressed, and the radial width of the bellows is reduced, further narrowing the local flow passage cross-sectional area. According to the principle of fluid continuity, this change will cause the flow rate to surge, causing the silicone oil to produce severe turbulent flow when passing through the narrow part, and the viscous resistance will increase. The dynamic pressure difference formed between the upstream and downstream of the flow passage is finally converted into a transient damping force acting on the bellows 23, realizing the secondary dissipation of impact energy.

[0057] In this process, the tapered cross section of the spiral channel 221 and the elastic deformation of the bellows 23 form a cooperative damping mechanism: the former strengthens the turbulent effect through geometric constraints, and the latter realizes adaptive adjustment of the flow passage through dynamic deformation, ultimately building a closed-loop vibration reduction system of "impact excitation-fluid energy dissipation-structure buffering".

[0058] In the related art, the bellows 23 in the mobile concrete mixing station supporting facility inclined aggregate batcher not only bears the dynamic shear stress generated by the flow of high-viscosity silicone oil, but also needs to resist the periodic external load brought by the vibration of the machine or the impact of the material. Due to the lack of an effective stress release mechanism, these two types of loads will form stress concentration at the peaks and valleys of the bellows 23, which will gradually cause micro fatigue cracks in the material as the number of working cycles increases. This cumulative damage will significantly shorten the fatigue life of the bellows 23.

[0059] Embodiment two, according to some embodiments of the present application, as Figures 9-13As shown, the fatigue suppression mechanism 3 is arranged on the side of the bellows 23, and the fatigue suppression mechanism 3 comprises a plurality of buffer assemblies 31 which are evenly distributed in the circumferential direction of the bellows 23. The buffer assembly 31 is provided with a sliding assembly 32 on the side away from the bellows 23. The buffer assembly 31 and the sliding assembly 32 are sleeved with an inner cylinder 33. The sliding assembly 32 is slidingly inserted into the inner cylinder 33. A plurality of support rings 34 are evenly arranged between the inner cylinder 33 and the outer shell 24.

[0060] It should be noted that, as Figure 6 As shown, the corrugated section of the bellows 23 is composed of a plurality of wave crest portions 233 and a plurality of wave trough portions 234.

[0061] As shown in Figure 11 and Figure 13 Each buffer assembly 31 is arranged in two rows in the axial direction of the bellows 23, and the buffer assemblies 31 in the two rows are staggered.

[0062] As shown in Figure 13 The buffer assembly 31 is an arc-shaped elastic beam 311, the concave surface of the arc-shaped elastic beam 311 faces the bellows 23, and the two ends of the arc-shaped elastic beam 311 are respectively hinged with a connecting pin 312. The two connecting pins 312 are respectively fixed to two wave crest portions 233, and the concave surface of the arc-shaped elastic beam 311 spans one wave crest portion 233.

[0063] It should be noted that the arc-shaped elastic beam 311 has deformation and reset capability.

[0064] It can be understood that in the specific embodiments of the present application, the two ends of the arc-shaped elastic beam 311 and the bellows 23 can rotate, so that when the bellows 23 is axially deformed, the arc-shaped elastic beam 311 will not interfere.

[0065] As shown in Figure 10 The sliding assembly 32 comprises a sliding pin 321, one end of the sliding pin 321 is fixedly connected with an inner limiting ring 322, the sliding pin 321 is fixedly sleeved with an outer limiting ring 323, the part of the sliding pin 321 extending out of the inner cylinder 33 is sleeved with an elastic member 324, the elastic member 324 is respectively abutted to the inner cylinder 33 and the outer limiting ring 323, and the end of the sliding pin 321 away from the inner limiting ring 322 is fixedly connected with a ball head 325. The ball head 325 is rotatably embedded in the convex surface of the arc-shaped elastic beam 311 to form a spherical pair.

[0066] It can be understood that the arc-shaped elastic beam 311 is deformed due to the deformation of the bellows 23, and when the two ends thereof are close to each other, the arc-shaped elastic beam 311 will change in radial length, so as to drive the sliding pin 321 to move a certain distance inside the inner wall of the inner cylinder 33. The existence of the elastic member 324 will reset the sliding pin 321. The spherical pair formed between the sliding pin 321 and the arc-shaped elastic beam 311 enables a certain degree of rotation between the sliding pin 321 and the arc-shaped elastic beam 311, avoiding motion interference during deformation.

[0067] As shown in Figure 11 and Figure 12 , a plurality of sliding pin mounting holes 331 are arranged on the inner wall of the inner cylinder 33, the sliding pin 321 is slidingly inserted into the sliding pin mounting hole 331, and the inner limiting ring 322 is used to prevent the sliding pin 321 from falling out of the sliding pin mounting hole 331.

[0068] It should be noted that the design of the sliding pin mounting hole 331 enables the sliding pin 321 and the inner limiting ring 322 to not only slide axially but also slide circumferentially. Therefore, it can be understood that the displacement of the sliding pin 321 can transmit the force borne by the bellows 23 to the inner cylinder 33, and distribute the stress circumferentially on the inner cylinder 33, avoiding stress concentration.

[0069] Further, the inner and outer sides of the support ring 34 abut against the inner cylinder 33 and the outer shell 24, respectively, and the support ring 34 is uniformly distributed with a plurality of honeycomb holes 341.

[0070] It can be understood that the inner cylinder 33 can be fixed inside the outer shell 24 by the support ring 34, and the stress can be dispersed and transmitted to the outer shell 24 by the plurality of honeycomb holes 341 designed on the support ring 34.

[0071] It can be further understood that the existence of the honeycomb hole 341 enables the support ring 34 to have a certain flexible deformation ability. When the stress is transmitted to the support ring 34 through the inner cylinder 33, the hole wall of the honeycomb hole 341 can be elastically deformed slightly, and part of the energy can be absorbed by local buckling or elastic compression of the material, so as to reduce the sudden change effect in the stress transmission process and realize gradual transmission of the load.

[0072] Therefore, in specific use, when the bellows 23 is axially compressed due to silicone oil stress or external impact, the peak portion 233 drives the connecting pin 312 to change position, and causes the arc-shaped elastic beam 311 to deform, specifically, the arc-shaped elastic beam 311 is arched radially due to the reduced distance between the two ends, and in this process, the arc-shaped elastic beam 311 absorbs part of the stress energy through its own elastic deformation, avoiding the bellows 23 directly bearing the entire load, at this time, the arc-shaped elastic beam 311 will push the sliding pin 321 to slide along the sliding pin mounting hole 331 to the inner cylinder 33, in this process, the elastic member 324 is compressed to store energy, at this time, the stress is transmitted to the inner cylinder 33 through the sliding pin 321, and is dispersed to the outer shell 24 through the honeycomb hole 341 of the support ring 34, avoiding stress concentration of the bellows 23, after impact attenuation, the elastic member 324 pushes the sliding pin 321 to reset, driving the arc-shaped elastic beam 311 to rebound, and the bellows 23 restores deformation, in this process, the flexible buffering of the arc-shaped elastic beam 311, the displacement release of the sliding assembly 32 and the stress dispersion of the support ring 34 form a synergistic mechanism to realize the fatigue damage suppression of the bellows 23, wherein the axial uniform distribution of the buffering assembly 31 and the design of the honeycomb hole 341 can ensure that the impact load in any direction can be effectively decomposed.

[0073] Further, in the process of deformation of the arc-shaped elastic beam 311, it will have a certain resistance, which, together with the resistance formed in the compression process of the elastic member 324, will generate a reverse supporting force on the bellows 23, which balances the pressure of the silicone oil and the impact load, avoiding excessive deformation of the bellows 23 leading to sudden change of damping force, forming a dynamic compensation mechanism.

[0074] The arc-shaped elastic beam 311 transmits part of the radial stress of the bellows 23 to the inner cylinder 33 through the sliding pin 321, and the remaining stress can be dissipated through the turbulence of the silicone oil, and the compression amount of the bellows 23 and the deformation amount of the arc-shaped elastic beam 311 are linearly related, synchronously adjusting the cross-sectional area of the silicone oil flow channel, forming self-adaptive response of impact intensity-damping force, avoiding over-damping or under-damping.

[0075] In the related art, the mobile concrete mixing station supporting facility inclined aggregate batching machine, when the silicone oil flows in the spiral channel 221, it will produce a certain damping effect, but if the vibration degree is relatively intense or the impact force is relatively intense, the viscous damping effect of the silicone oil in the variable cross-section spiral channel 221 is not enough to dissipate the impact energy.

[0076] In some embodiments of the present application, as shown in Figure 14 and Figure 15 , a plurality of bosses 222 are arranged in the spiral channel 221, the plurality of bosses 222 are distributed in a spiral shape along the spiral channel 221, and the plurality of bosses 222 are distributed in an increasing number from one end of the spiral channel 221 to the other end.

[0077] It should be noted that the two ends of the boss 222 along the spiral track direction of the spiral channel 221 are arranged in a circular arc shape.

[0078] Specifically, the size of the boss 222 is reduced correspondingly with the reduction of the width of the spiral channel 221.

[0079] Further, a groove 223 is arranged in the spiral channel 221, and the groove 223 is arranged along the spiral track of the spiral channel 221.

[0080] Therefore, when the silicone oil flows in the spiral channel 221, the circular arc cross section of the boss 222 can induce the Karman vortex street when the fluid passes through, so that the turbulent dissipation rate is significantly improved. The number and size of the boss 222 along the spiral channel 221 are arranged, and the variable cross section design of the spiral channel 221 itself forms a composite throttling effect. When the silicone oil generates pulse flow due to severe impact, the gap between the boss 222 and the spiral channel 221 forces the fluid to contract and expand multiple times. According to Bernoulli's equation, the pressure difference between the upstream and downstream of the flow passage will increase suddenly. The nonlinear growth of this pressure gradient makes the transient damping force acting on the bellows 23 have the self-adaptive characteristic that "the stronger the impact, the greater the resistance". The damping saturation phenomenon of the simple variable cross section channel under extreme working conditions is avoided. At the same time, the distribution density design of the boss 222 enables it to dissipate vibration energy of different frequencies. Through the intervention of the boss 222, the damping mechanism of the spiral channel 221 is upgraded from a single "variable cross section viscous damping" to a "boss 222 induced turbulence + dynamic throttling + multi-frequency dissipation" composite damping system. The design of the groove 223 in the present application forms a secondary vortex inside when the fluid passes through, which can effectively enhance the suppression of low-frequency large-amplitude vibration. At the same time, the existence of the groove 223 can guide the silicone oil to smoothly bypass the boss 222, avoiding the occurrence of dead zone vortex, and can also accelerate the flow of silicone oil, compensating for the damping attenuation caused by the size reduction of the boss 222.

[0081] It should be noted that the specific model and specification of the horizontal inclined angle belt conveyor 1, the aggregate storage bin 12, the aggregate measuring hopper 13 and the elastic member 324 need to be selected and determined according to the actual specifications of the device. The specific selection and calculation method adopts the existing technology in the art, and therefore will not be described in detail.

[0082] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto. Any person skilled in the art can easily think of changes or replacements within the technical scope disclosed in the present application, which should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A mobile concrete mixing station supporting facility inclined aggregate batching machine, comprising a horizontal inclined belt conveyor (1), wherein the horizontal section of the horizontal inclined belt conveyor (1) is provided with a frame (11), and the frame (11) is provided with multiple groups of aggregate storage bins (12), and each group of aggregate storage bins (12) is provided with an aggregate measuring hopper (13) at the bottom end, characterized in that: The horizontally inclined belt conveyor (1) is provided with a plurality of belt rollers (2), the belt rollers (2) comprising an axis roller (21) rotatably connected to a bracket, a sleeve (22) being fixedly sleeved on the axis roller (21), a bellows (23) being provided on the outer sleeve of the sleeve (22), the inner wall of the bellows (23) and the outer wall of the sleeve (22) being gap-fitted, the bellows (23) and the sleeve (22) being flexibly sealed at both ends, an outer shell (24) being provided on the outer side of the bellows (23), and the outer shell (24) being fixedly sleeved on the axis roller (21); The bellows (23) and the sleeve (22) are filled with high-viscosity silicone oil; The outer wall of the sleeve (22) is provided with a spiral channel (221) with a variable cross-section.

2. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 1, characterized in that: The space between the sleeve (22) and the bellows (23) constitutes a fluid damping channel.

3. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 1, characterized in that: The spiral channel (221) is arranged with equal pitch and equal diameter depth, and the spiral channel (221) penetrates both ends of the sleeve (22) along the axial direction.

4. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 1, characterized in that: The width of the spiral channel (221) is gradually changed.

5. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 1, characterized in that: The bellows (23) adopts a metal structure, and the bellows (23) has deformation capability.

6. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 1, characterized in that: End covers (231) are symmetrically provided at both ends of the bellows (23) and the sleeve (22), and the end covers (231) are sealingly and slidably sleeved on the axial roller (21).

7. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 6, characterized in that: A sealing ring (232) is coaxially arranged on the inner side of the end cover (231), and the sealing ring (232) is in sealing contact with the bellows (23) and the sleeve (22).

8. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 7, characterized in that: The sealing ring (232) is hollow inside.

9. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 1, characterized in that: The bellows (23) undergoes axial and radial deformation after the belt roller (2) is impacted, and changes the size of the fluid damping channel.

10. The mobile concrete mixing station supporting facility inclined aggregate batching machine according to claim 1, characterized in that: The high-viscosity silicone oil flows in the fluid damping channel after the belt roller (2) is impacted, and generates viscous damping when flowing along the spiral channel (221).

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