A climbing conveying mechanism of a conveying device and a multi-section telescopic conveying device

Abstract

The application discloses a climbing conveying mechanism of a conveying device and a multi-section telescopic conveying device. The climbing conveying mechanism is arranged between adjacent body sections and comprises a front roller and a gap maintaining unit. The front roller is arranged corresponding to the front side of the conveying direction of the transport body section through the gap maintaining unit, and the diameter of the front roller is smaller than the diameter of the conveying roller. The gap maintaining unit maintains the preset gap between the front roller and the conveying belt of the previous body section. The front roller receives the driving force of the corresponding power source to rotate actively, lifts the conveyed material upward from the conveying belt of the previous body section through the friction force to form the first-stage climbing action, and cooperates with the conveying belt of the previous body section and the corresponding transport body section to continue conveying the conveyed material to the corresponding transport body section to form the second-stage climbing action. The total height of single climbing is decomposed into two stages of climbing, the climbing is more stable, and the conveying stability is high.

Description

Technical Field

[0001] This invention belongs to the field of conveying equipment technology, and particularly relates to a climbing conveying mechanism and a multi-section telescopic conveying device. Background Technology

[0002] Drawer-type multi-section telescopic conveyors are widely used for long-distance and incline material transport. Traditional telescopic conveyors often use large-diameter conveyor rollers to directly drive the conveyor belt. While their structure is simple and the transmission is direct, they have significant technical drawbacks in multi-section stacking and incline operation scenarios. The large bending radius of the large-diameter conveyor rollers results in a thicker conveyor belt (e.g., up to approximately 60 mm). When multiple sections extend and retract layer by layer, climbing in stages, a significant height difference is created between the conveyor surfaces of adjacent sections. For example, the height difference increases when the subsequent section is descending relative to the preceding section, and decreases when it is ascending relative to the preceding section. For smaller materials, this height difference exceeds the material's own height, making it difficult to effectively lift the material when transitioning from one section to the next, easily causing problems such as material breakage and jamming. In addition, the conveyor belt in the feeding section needs to have wear resistance during long-term use. Its surface friction coefficient is usually low. Under climbing conditions, the friction between the conveyor belt surface and the conveyed material is insufficient to stably drive the material upward. The material is prone to slipping or even rolling backward on the climbing section, affecting the stability of the conveying. Summary of the Invention

[0003] To address at least one of the aforementioned problems, this application provides an inclined conveying mechanism and a multi-section telescopic conveying device. The inclined conveying mechanism is arranged between adjacent machine sections and includes a front roller and a gap-maintaining unit. The front roller is positioned at the front of the conveying machine section in the conveying direction via the gap-maintaining unit, and its diameter is smaller than the diameter of the conveying roller of the conveying machine section. The gap-maintaining unit is configured to maintain a preset distance between the front roller and the conveyor belt of the preceding machine section. The front roller is configured to receive driving force from the power source of the conveying machine section and rotate actively to lift a portion of the conveyed material from the conveyor belt of the preceding machine section upwards through friction, forming a first-stage climbing action; and the front roller is configured to cooperate with the conveyor belt of the preceding machine section and the conveyor belt of the current machine section to continue transporting the conveyed material to the current machine section, forming a second-stage climbing action.

[0004] In one or more embodiments, a lifting structure is provided on the outer ring surface of the front roller, the lifting structure being configured to contact the conveyed material to lift the conveyed material upward by friction.

[0005] In one or more embodiments, the lifting structure includes a plurality of teeth arranged circumferentially at intervals on the outer ring surface of the front roller, each tooth being configured to sequentially enter the contact area between the surface of the conveyed material and the front roller as the front roller rotates, so as to lift the conveyed material upward by friction and drive it along the conveying direction.

[0006] In one or more embodiments, the tooth includes a front tooth surface located on the side in front of the rotation direction of the front roller and a rear tooth surface located on the side behind, the rear tooth surface being configured to be inclined along the tooth root to the tooth tip toward the rotation direction of the front roller.

[0007] In one or more embodiments, the plane containing the front tooth surface coincides with the rotation axis of the front roller.

[0008] In one or more embodiments, the gap maintaining unit includes two support members arranged at intervals, the first ends of the two support members being rotatably connected to the conveyor body section, and the second ends of the two support members being respectively supported on both sides of the preceding body section in the width direction of the conveyor belt; wherein, the front roller is rotatably connected between the two support members.

[0009] In one or more embodiments, the gap maintaining unit further includes a support wheel mounted on the second end of the support member, the support wheel being configured to roll support the preceding fuselage section; The front roller is configured to maintain a constant preset distance between itself and the conveyor belt of the preceding section by means of the rolling support of the support wheel and the swing of the support relative to the corresponding transport section.

[0010] In one or more embodiments, the climb height of the first stage of climbing is A, the climb height of the second stage of climbing is B, and the ratio of A / B ranges from 0.3 to 0.7.

[0011] In one or more embodiments, the diameter of the front roller is selected such that the preset spacing is less than the minimum size of the conveyed material, so that the conveyed material can transition from the conveyor belt of the previous machine section to the conveyor belt of the transport machine section via the front roller.

[0012] Based on the same inventive concept, this application also provides a multi-section telescopic conveying device, including an inclined conveying mechanism as described in any of the above-mentioned conveying devices.

[0013] Because the present invention adopts the above technical solution, it has the following advantages and positive effects compared with the prior art: In one embodiment of the present invention, a front roller is positioned at the front end of the conveyor section via a gap-maintaining unit. The diameter of the front roller is smaller than that of the conveyor roller, effectively reducing the height difference between the conveyor surfaces of the feeding section and the conveyor section. The front roller lifts the conveyed material to achieve the first-stage climbing action, and continues to work with the front and rear conveyor belts to complete the second-stage climbing action. The total height of a single climb between adjacent sections is decomposed into the first-stage climbing achieved by the front roller and the second-stage climbing achieved by the subsequent conveyor belts. This significantly reduces the climbing height of each stage relative to the total height, resulting in less conveying resistance for the material during the climbing process, a smoother climb, and higher conveying stability. Furthermore, the gap-maintaining unit maintains a relatively constant preset distance between the front roller and the conveyor belt of the preceding section. When the preceding section extends, retracts, or tilts relative to the conveyor section, the gap-maintaining unit remains supported on the platform of the preceding section. This ensures that the height of the first-stage climbing remains stable regardless of the tilt of the conveyor, guaranteeing the stability and reliability of the climbing conveyor.

[0014] Furthermore, the total height of a single climb between adjacent machine sections is decomposed into a first-stage climb achieved by the front roller and a second-stage climb achieved by the subsequent conveyor belt. This allows smaller materials to be smoothly transferred from the conveyor belt of the previous machine section to the conveyor belt of the transport machine section, solving the problem in the traditional large roller scheme where small materials cannot be climbed and transported due to excessive height differences between sections.

[0015] Furthermore, in one embodiment of the present invention, an actively rotating front roller is positioned between adjacent machine sections, utilizing a two-stage climbing mechanism to decompose the total height of a single climb into two progressively increasing levels. The front roller is configured to rotate actively and actively contact and drive the conveyed material through its lifting structure on its outer ring surface. This active drive of the front roller compensates for the frictional deficiencies of the conveyor belt in the feeding section under climbing conditions, ensuring that the conveyed material receives a stable upward driving force throughout the lifting process. This guarantees that the material can reliably complete the transition from the first to the second stage of climbing, thereby solving the technical problem in traditional solutions where the low friction characteristics of the feeding section belt cause material slippage on the climbing section, making it difficult to convey to the next stage of the conveyor. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the inclined conveying mechanism of the conveying equipment according to Embodiment 1 of the present invention; Figure 2 This is another schematic diagram of the inclined conveying mechanism of the conveying equipment according to Embodiment 1 of the present invention; Figure 3 This is a cross-sectional view of the lifting structure of the inclined conveying mechanism of the conveying equipment according to Embodiment 1 of the present invention; Figure 4This is a schematic diagram of the retracted state of the multi-section telescopic conveyor device according to Embodiment 1 of the present invention; Figure 5 This is a schematic diagram of the multi-section telescopic conveyor in the climbing state of the machine body in Embodiment 1 of the present invention; Figure 6 This is a schematic diagram of the multi-section telescopic conveyor in the climbing state of the machine body in Embodiment 3 of the present invention; Figure 7 This is a schematic diagram of the retracted state of the multi-section telescopic conveyor device according to Embodiment 3 of the present invention; Figure 8 This is a schematic diagram of the multi-section telescopic conveyor device in the fully opened state according to Embodiment 3 of the present invention; Figure 9 This is a schematic diagram of a single section of the multi-section telescopic conveyor system according to Embodiment 3 of the present invention; Figure 10 This is a schematic diagram showing the unlocking state of the locking mechanism of the multi-section telescopic conveyor device according to Embodiment 3 of the present invention; Figure 11 This is a schematic diagram of the locking state of the locking mechanism of the multi-section telescopic conveyor device according to Embodiment 3 of the present invention; Figure 12 This is a schematic diagram of the side guide section of the multi-section telescopic conveyor device according to Embodiment 3 of the present invention; Figure 13 This is a schematic diagram of the supporting unit and the bottom guide portion of the multi-section telescopic conveyor device according to Embodiment 3 of the present invention; Figure 14 This is a schematic diagram of the multi-section telescopic conveyor device of Embodiment 4 of the present invention in a preset initial state; Figure 15 This is a schematic diagram of the multi-section telescopic conveyor device of Embodiment 4 of the present invention when all sections of the machine body are extended into place; Figure 16 This is a partial schematic diagram of the front end of the first section of the multi-section telescopic conveyor in Embodiment 4 of the present invention; Figure 17 This is a partial schematic diagram of one section of the multi-section telescopic conveyor device according to Embodiment 4 of the present invention; Figure 18 This is a schematic diagram of the ground rail guide unit entering the guide rail in the multi-section telescopic conveyor device of Embodiment 4 of the present invention.

[0017] Explanation of reference numerals in the attached drawings: 1. Feeding machine body section; 2. Conveying machine body section; 3. Conveyor belt; 4. Front roller; 5. Gap maintaining unit; 51. Support component; 52. Support wheel; 6. Tooth; 61. Front tooth surface; 62. Rear tooth surface; 301. Machine body section; 311. First machine body section; 302. Telescopic power unit; 331. Drive unit; 332. Locking component; 333a. First mating part; 333b. The first mating part. 2. Parts; 304. Support unit; 341. Support roller; 342. Support component; 305. Side guide part; 351. Side guide wheel; 306. Bottom guide part; 361. Guide mating component; 401. First fuselage section; 402. Power wheel; 403. Support wheel; 404. Travel drive; 405. Drive shaft; 406. Auxiliary travel component; 407. Guide rail; 408. Ground rail guide wheel. Detailed Implementation

[0018] The embodiments of this application will be further described in detail below with reference to the accompanying drawings and examples. The detailed description of the following embodiments and the accompanying drawings are used to illustrate the principles of this application by way of example, but should not be used to limit the scope of this application. This application can be implemented in many different forms and is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

[0019] These embodiments are provided to make the application thorough and complete, and to fully express the scope of the application to those skilled in the art. It should be noted that, unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of components and steps illustrated in these embodiments should be interpreted as merely exemplary and not as limiting.

[0020] All terms used in this application have the same meaning as understood by one of ordinary skill in the art to which this application pertains, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries should be interpreted as having meanings consistent with their meanings in the context of the relevant art, and not as idealized or highly formalized, unless expressly defined herein.

[0021] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, they should be considered part of the specification.

[0022] Example 1 Before describing this application, the following explanation is given for certain terms.

[0023] The multi-section telescopic conveyor in this application refers to a conveyor system composed of multiple body sections arranged sequentially along the telescopic direction. Each body section includes a feeding body section for receiving the material being conveyed and at least one transport body section for continuing to convey the material along the conveying direction. Each body section can be relatively displaced along the telescopic direction to change the overall length of the equipment. Inclined conveying refers to the conveying process where material needs to pass through a transition area with a height difference between adjacent body sections. In this application, "previous body section" refers to the one further forward along the conveying direction among two adjacent body sections, and "corresponding transport body section" refers to the latter body section among two adjacent body sections that receives the material being conveyed. The first-stage climb refers to the process of the material being lifted from the conveyor belt of the previous body section to the front roller, and the second-stage climb refers to the process of the material continuing to be conveyed from the front roller to the conveyor belt of the corresponding transport body section.

[0024] The technical solution of this application will now be described with reference to the accompanying drawings.

[0025] See Figures 1 to 5 In one embodiment, this application provides an inclined conveying mechanism for a conveying device, which is applied to a multi-section telescopic conveyor. The multi-section telescopic conveyor includes multiple body sections arranged sequentially, including a feeding body section 1 for loading materials and at least one transport body section 2. Each body section is equipped with a conveyor belt 3 driven by conveyor rollers, which are driven to rotate by a corresponding power source. The specific form of the power source is not limited in this application; it can be a servo motor, a frequency converter motor, or a hydraulic motor, or other commonly used drive devices in the art. The power source can transmit power to the conveyor rollers through conventional transmission methods such as chain drive, belt drive, or gear drive; this application does not impose specific limitations on this.

[0026] The inclined conveyor mechanism is arranged between adjacent machine sections (e.g., between the feeding machine section and the first conveyor section, or between adjacent conveyor sections), and specifically may include a front roller 4 and a gap maintaining unit 5. The front roller 4 is positioned at the front of the conveyor section 2 in the conveying direction via the gap maintaining unit 5, and the diameter of the front roller 4 is smaller than the diameter of the conveying roller of the conveyor section 2. The gap maintaining unit 5 is configured to maintain a preset distance between the front roller 4 and the conveyor belt 3 of the preceding machine section.

[0027] In this design, the front roller 4 is configured to receive driving force from the power source of the conveyor section 2 and rotate actively to lift part of the conveyed material from the conveyor belt 3 of the preceding section through friction, forming the first stage of the climbing action. Simultaneously, the front roller 4 is configured to work in conjunction with the conveyor belt 3 of both the preceding and preceding sections to continue transporting the conveyed material to the conveyor belt 3 of the conveyor section 2, forming the second stage of the climbing action. By decomposing the total height of a single climb between adjacent sections into the first stage of climbing achieved by the front roller 4 and the second stage of climbing achieved by the conveyor belt 3 of the conveyor section 2, the climbing height of each stage is significantly reduced relative to the total height, resulting in less conveying resistance for the material during the climbing process and a smoother climb.

[0028] Specifically, the front roller 4 receives driving force from the power source of the conveyor body section 2 and rotates actively. It can obtain rotational power from the power source of the conveyor body section 2 or the conveyor roller through an additional transmission device (such as a chain, synchronous belt, gear set, etc.), so that the front roller 4 and the conveyor belt 3 of the conveyor body section 2 operate synchronously. Since the front roller 4 rotates actively rather than passively, it can provide a continuous upward driving force for the conveyed material, rather than relying solely on the pushing of the conveyor belt 3.

[0029] The specific structure of the inclined conveying mechanism in this embodiment will be further described below: See Figure 3 In this embodiment, a lifting structure is provided on the outer ring surface of the front roller 4. The lifting structure is configured to contact the conveyed material to lift a portion of the conveyed material upward through friction. Compared to a conventional smooth roller surface, the lifting structure can significantly increase the contact friction between the material and the conveyed material, providing a stable and reliable upward driving force for the material under incline conditions.

[0030] Specifically, the front roller 4 may include a cylinder and a rubber layer formed on the outer ring surface of the cylinder, on which the aforementioned lifting structure is formed. The cylinder may be made of a metal material (such as steel or aluminum alloy) to ensure the overall rigidity and load-bearing capacity of the front roller 4; the rubber layer covers the outer ring surface of the cylinder and can be bonded to the cylinder through a vulcanization process.

[0031] Furthermore, the lifting structure includes a plurality of teeth 6 arranged circumferentially on the outer surface of the front roller 4 (the teeth 6 may be made of rubber material, i.e., integrally formed on the outer surface of a rubber layer, with a plurality of raised teeth 6 formed circumferentially on the outer surface of the rubber layer). Each tooth 6 is configured to sequentially enter the contact area between the surface of the conveyed material and the front roller 4 when the front roller 4 rotates, so as to lift the conveyed material upward by friction and drive it along the conveying direction. In a specific implementation, as the front roller 4 rotates, adjacent teeth 6 sequentially contact the lower surface of the conveyed material, forming an effect similar to "catching" the material and pushing it upward.

[0032] See Figure 3 Specifically, the tooth portion 6 includes a front tooth surface 61 located in front of the front roller 4 in the rotation direction and a rear tooth surface 62 located behind it. The rear tooth surface 62 is configured to be inclined along the tooth root to the tooth tip in the rotation direction of the front roller 4. Figure 3 In the orientation shown, the front roller 4 rotates counterclockwise, and the rear tooth surface 62 tilts outward counterclockwise from the root of the tooth. This tilting direction causes the normal component of the contact force to point in the direction of material movement when the rear tooth surface 62 contacts the conveyed material, which can more effectively convert the frictional force into a lifting driving force for the material.

[0033] Furthermore, the plane containing the front tooth surface 61 coincides with the rotation axis of the front roller 4. This means that the front tooth surface 61 extends radially along the front roller 4, and when the tooth 6 disengages from the conveyed material, the front tooth surface 61 will not obstruct or drag the material, allowing the tooth 6 to smoothly disengage.

[0034] See Figure 1 and Figure 2 In this embodiment, the gap maintaining unit 5 may specifically include two support members 51 arranged at intervals. The first ends of both support members 51 are rotatably connected to the corresponding conveyor body section 2, and the second ends of the two support members 51 are respectively supported on both sides of the conveyor belt 3 of the preceding body section in the width direction (specifically, supported on two guide rails arranged along the conveying direction on both sides of the conveyor belt). The front roller 4 is rotatably connected between the two support members 51. By rotatably connecting the support members 51 to the corresponding conveyor body section 2, the gap maintaining unit 5 as a whole can swing around the first end of the support member 51, and adaptively follow and adjust when the corresponding conveyor body section 2 undergoes pitch changes relative to the preceding body section.

[0035] Furthermore, the gap maintaining unit 5 also includes a support wheel 52 mounted on the second end of the support member 51. The support wheel 52 is configured to roll and support the preceding machine section. The front roller 4 is configured to maintain a constant preset gap with the conveyor belt 3 of the preceding machine section by relying on the rolling support of the support wheel 52 and the swing of the support member 51 relative to the corresponding conveyor section 2. Specifically, the support wheel 52 is always pressed against the platform of the preceding machine section. When the corresponding conveyor section 2 undergoes extension or pitch displacement relative to the preceding machine section (i.e., when the gap between the corresponding conveyor section 2 and the preceding machine section changes in the height direction), the support member 51 swings around its first end, and the second end of the support member 51 can then always remain supported on the preceding machine section, so that the front roller 4 on the support member 51 can always maintain its relative position with the conveyor belt 3 of the preceding machine section (i.e., maintain a constant preset gap between the front roller 4 and the conveyor belt 3 of the preceding machine section). This floating adaptive design ensures that the height of the first-stage climb remains stable regardless of the pitch of the fuselage, guaranteeing the stability of the incline transport.

[0036] It is important to emphasize that the fundamental purpose of the gap maintaining unit 5 in this embodiment is not merely to maintain the distance between the front roller 4 and the conveyor belt 3 of the preceding machine section, but rather to enable the inclined conveying mechanism of this application to be adapted to multi-section telescopic conveyor equipment with inclined scenarios. Under normal planar conveying conditions of multi-section telescopic conveyor equipment, only basic alignment of the conveying surfaces is required between adjacent machine sections. Even if the distance between the conveying surfaces fluctuates within a certain range, it usually does not have a substantial impact on material conveying. However, in inclined scenarios, a significant change in pitch angle will occur between the front and rear ends of the corresponding conveyor section 2 (the greater the climbing height of one end of the conveyor section, the more severe its overall tilt). At this point, if the distance between the front roller and the conveyor belt of the preceding machine section is not actively constrained, this distance will dynamically change with the pitch of the conveyor section: when the conveyor section tilts upward, the height of the front roller 4 relative to the conveyor belt of the preceding machine section increases, which will lead to an increase in the height of the first-stage climb; when the conveyor section tilts downward, this distance may decrease to the point where the front roller and the conveyor belt of the preceding machine section come into contact and interfere. This dynamic change in distance will directly disrupt the height distribution relationship between the two stages of climb, causing the height of the first-stage climb to fluctuate, and the stress state of the conveyed material during the climb to be unstable. In severe cases, it may even lead to the material not being effectively lifted or getting stuck between the front roller and the conveyor belt of the preceding machine section.

[0037] In traditional large roller conveyor systems, due to the large space occupied by the large-diameter rollers and the limited bending radius of the conveyor belt, designers typically focus on how to achieve smooth connection between the conveyor surfaces of adjacent sections under high-drop conditions by adding leveling mechanisms. However, they often overlook the impact of gap fluctuations at the connection point on material climbing stability in incline scenarios. This is because, in traditional systems, there is an inherent, unavoidable large gap between the end of the previous conveyor belt and the beginning of the next, caused by the large diameter of the rollers. The impact of this gap fluctuation on the material is masked by the large gap itself. This application's design takes a completely different approach: since the diameter of the front roller is actively reduced to decrease the inter-section gap, the stability control of the reduced gap becomes crucial. The change in gap, relative to the absolute value of the reduced gap, accounts for a significant proportion and directly affects the stability of the first-stage climbing height, thereby disrupting the height distribution between the two stages of climbing. Based on this understanding, this application incorporates a gap-maintaining unit 5. The swinging of the support member 51 around its first end and the rolling support of the support wheel 52 on the platform of the preceding machine section ensure that the gap between the front roller 4 and the conveyor belt 3 of the preceding machine section remains stable regardless of the pitch changes of the corresponding transport machine section 2 during the climbing process. Thus, the height of the first-stage climb is limited, the height distribution between the two stages of climb is stably maintained, and the overall operational reliability of the climbing conveyor mechanism is guaranteed.

[0038] In this embodiment, the ratio A / B between the first-stage climbing height A and the second-stage climbing height B is between 0.3 and 0.7. The first-stage climbing height A is determined by the preset distance between the front roller 4 and the conveyor belt 3 of the preceding machine body section, and the second-stage climbing height B is determined by the height difference between the front roller 4 and the conveyor belt 3 of the corresponding transport machine body section 2. When the ratio A / B is controlled within the range of 0.3 to 0.7, the load distribution of the two stages of climbing is relatively balanced: the height of the first-stage climbing is not too large, which would make it difficult to lift the material, and the height of the second-stage climbing is not too large, which would make the friction of the conveyor belt insufficient to drive the material, thereby achieving the optimal overall conveying efficiency of the two stages of climbing.

[0039] Furthermore, the diameter of the front roller 4 is selected such that the preset distance is smaller than the smallest size of the conveyed material. Specifically, for multi-size mixed-line conveying applications, the conveyed materials may have various different sizes (e.g., large-size car tires and small-size motorcycle tires). By selecting the diameter of the front roller 4 such that the preset distance between it and the preceding conveyor belt 3 is smaller than the height of the smallest size of the conveyed material, it can be ensured that even the smallest size material can be effectively contacted and lifted by the lifting structure of the front roller 4. This allows the conveyed material to smoothly transition from the preceding conveyor belt 3 to the corresponding conveyor belt 3 of the transport section 2 via the front roller 4, achieving fully compatible incline conveying.

[0040] The two-stage climbing process of this embodiment will be described below.

[0041] In the first-stage climbing phase, the front roller 4 rotates actively under the drive of the power source of the corresponding conveyor section 2. The lifting structure (e.g., teeth 6) set on the outer ring surface of the front roller 4 contacts the lower surface of the conveyed material, and lifts part of the conveyed material from the conveyor belt 3 of the preceding section upward through friction. The front end of the lifted conveyed material first contacts the outer ring surface of the front roller 4, and then, as the front roller 4 continues to rotate, the conveyed material is gradually lifted upward and moves forward under the push of the conveyor belt 3 of the preceding section until its main body transitions from the conveyor belt 3 of the preceding section to the front roller 4, completing the first-stage climbing action.

[0042] In the second-stage climbing phase, the front roller 4 continues to rotate, working in conjunction with the conveyor belt 3 of the preceding machine section (pushing forward) and the conveyor belt 3 at the corresponding conveyor roller section 2, which, through friction, propels the material from the front roller 4 onto the conveyor belt 3 of the corresponding conveyor section 2, completing the second-stage climbing action. Thus, the material has completed the entire transition from the preceding machine section to the conveyor section through two stages of climbing.

[0043] It should also be noted that the active rotation of the front roller 4 and the provision of a lifting structure in this embodiment are closely related to the differences in conveyor belt characteristics between the feeding section and the main conveying section of the multi-section telescopic conveyor. In the scenario where the preceding section is the feeding section 1, the feeding section 1 receives the material being conveyed. The material is typically thrown or dumped onto the conveyor belt 3 of the feeding section 1 from a certain height. The material's velocity upon contact with the conveyor belt 3 is zero or far lower than the belt's operating speed. Therefore, relative slippage inevitably occurs during the acceleration process to synchronize with the conveyor belt 3. To cope with this continuous sliding wear, the conveyor belt 3 of the feeding section 1 is typically made of a wear-resistant belt with superior wear resistance to ensure its service life under long-term material sliding friction conditions. However, the surface friction coefficient of wear-resistant belts is usually low (an inherent characteristic of wear-resistant materials), resulting in relatively limited frictional force that the conveyor belt 3 of the feeding section 1 can provide when conveying materials. In contrast, the conveyor belt 3 of the main conveying section (i.e., the conveyor body section 2) can be a friction belt with a higher surface friction coefficient. This is because the material in the main conveying section has been accelerated to be synchronized with the conveyor belt 3, and there is almost no relative sliding. The wear of the conveyor belt is greatly reduced, and the requirements for wear resistance are correspondingly reduced. Therefore, materials with a higher friction coefficient can be used to ensure the stability of the material during the conveying process.

[0044] This difference in conveyor belt characteristics reveals a prominent technical contradiction under incline conditions. When the conveyed material reaches the end of the conveyor belt 3 of the loading machine section 1 and prepares to perform the first stage of climbing, the front end of the material is lifted by the front roller 4. One side of the material (the part closer to the lifted side in the width direction) gradually detaches from the surface of the conveyor belt 3 of the loading machine section 1, significantly reducing the actual contact area between the material and the conveyor belt 3 of the loading machine section 1. Since the surface friction coefficient of the conveyor belt 3 of the loading machine section 1 is already low, coupled with the further reduction in contact area, the conveyor belt 3 of the loading machine section 1 can hardly provide effective forward and upward driving force for the material at this point. That is, relying solely on the friction of the conveyor belt 3 of the loading machine section 1, the material not only cannot complete the climb but may also slip or even roll backward on the slope. In traditional solutions, due to the lack of a structure to provide active drive for the front end of the material, this contradiction cannot be overcome, and conveying failures on inclines become commonplace. In this embodiment, since the front roller 4 is configured to rotate actively and actively contact and drive the conveyed material through the lifting structure (e.g., rubber teeth 6) on its outer ring surface, the upward gripping force provided by the front roller 4 replaces the friction force lost by the conveyor belt 3 of the feeding machine section 1 after the material is lifted. In other words, the active drive of the front roller 4 compensates for the friction deficiency of the conveyor belt 3 of the feeding machine section 1 under climbing conditions, so that the conveyed material is always subjected to a stable upward driving force during the lifting process, ensuring that the material can reliably complete the transition from the first level of climbing to the second level of climbing, thereby solving the technical problem in the traditional solution where the material slips in the climbing section due to the low friction characteristics of the feeding section belt, making it difficult to convey to the next level of the conveyor body.

[0045] Example 2 Based on the same concept, this embodiment provides a multi-section telescopic conveyor device, including the climbing conveyor mechanism of the multi-section telescopic conveyor device in the above embodiment one.

[0046] Example 3 This embodiment further explains the overall structure and working method of the multi-section telescopic conveyor's body sections in Embodiments 1 and 2, including their extension, locking, climbing, and guiding reset. It should be noted that this embodiment describes the collaborative working mechanism of extension and climbing between multiple body sections from the perspective of the entire equipment. The "extending direction" in this embodiment refers to the direction in which the body section expands outward from its retracted state, which is opposite to the conveying direction in Embodiment 1—in Embodiment 1, material is conveyed along the conveying direction from the feeding body section near the fixed end of the equipment to the transport body section away from the fixed end; during the extension process, the body section extends outward in the opposite direction. In this embodiment, "the preceding body section" and "the following body section" refer to the one further forward and the one further back in the extending direction among two adjacent body sections. The climbing action described in this embodiment refers to the process in which the front end of the body section undergoes vertical displacement relative to the rear end in the extending direction when passing through a slope area with a height difference.

[0047] See Figures 6 to 13 In this embodiment, the multi-section telescopic conveyor includes multiple body sections 301, a telescopic power unit 302, a locking mechanism, and a supporting unit 304. The multiple body sections 301 are sequentially nested along the telescopic direction, and each body section 301 can be relatively displaced along the telescopic direction, thereby realizing the segmented telescopic movement of the entire machine. Among the multiple body sections 301, the one located at the foremost end in the extension direction is the first body section 311, and the others are sequentially the next body sections.

[0048] A telescopic power unit 302 is disposed on the first fuselage section 311, used to drive each fuselage section 301 to extend or retract relative to the adjacent subsequent fuselage section. A locking mechanism is correspondingly disposed between two adjacent fuselage sections 301, used to lock the preceding fuselage section to the following fuselage section after the two adjacent fuselage sections have been displaced to a preset relative position. A support unit 304 is disposed on each fuselage section 301, used to provide a fulcrum support for the preceding fuselage section relative to the following fuselage section when the preceding fuselage section is in the locked state.

[0049] In this embodiment, the telescopic power unit 302 is configured to, after the first fuselage section 311 is locked, drive the adjacent subsequent fuselage section to move through the locked fuselage section, and the corresponding locking mechanism locks the fuselage section 301 after it has moved to a preset relative position. This allows each fuselage section 301 to be selectively driven to extend one by one according to the needs of the climbing position and locked after extending, or to be selectively driven to retract one by one and locked after retracting. This allows each fuselage section 301 to independently perform an extension climbing action or a retraction descending action relative to the adjacent subsequent fuselage section in the locked state with the help of the support unit 304. The support unit 304 is configured to provide fulcrum support relative to the subsequent fuselage section when the preceding fuselage section is locked, so as to limit the vertical offset of the rear end of the preceding fuselage section within a preset range when the preceding fuselage section performs a climbing or descending action.

[0050] This embodiment achieves independent displacement and locking of each fuselage section by using a telescopic power unit to drive the extension of the fuselage sections and locking them at preset relative positions by a locking mechanism. This ensures that each fuselage section is in a locked state after displacement, providing a structural foundation for subsequent independent climbing. A support unit provides a fulcrum for the preceding fuselage section relative to the following fuselage section in the locked state, allowing the preceding fuselage section to independently perform extension climbing or retraction descent movements using this support unit as a fulcrum. This transforms the significant interference problem caused by the entire machine climbing as a whole in traditional solutions into each fuselage section independently absorbing changes in climbing height within its own length range. This allows the equipment to complete large-span climbing without interference between sections. Simultaneously, independent climbing section by section significantly reduces the load per operation, resulting in smoother and more stable equipment operation.

[0051] The specific structure of the conveying device in this embodiment will be further described below: See Figure 10 and Figure 11 In this embodiment, the locking mechanism may specifically include a drive unit 331 disposed on the rear fuselage section and a locking member 332 driven by the drive unit 331. The front fuselage section is provided with a first mating part 333a and a second mating part 333b corresponding to and cooperating with the locking member 332. The first mating part 333a is disposed at the rear end of the front fuselage section, and the second mating part 333b is disposed at the front end of the front fuselage section. The drive unit 331 is used to drive the locking member 332 to extend into the first mating part 333a to lock the extended front fuselage section to the rear fuselage section, or to drive the locking member 332 to extend into the second mating part 333b to lock the retracted front fuselage section to the rear fuselage section, or to drive the locking member 332 to exit the first mating part 333a or the second mating part 333b to release the locking between the front and rear fuselage sections. Figure 10The unlocked state of the locking mechanism is shown. Figure 11 The locked state of the locking mechanism is shown.

[0052] Specifically, the drive unit 331 can be a motion mechanism such as a servo electric cylinder, a pneumatic cylinder, or an electric push rod, and the locking member 332 is a pin connected to the servo electric cylinder for transmission. The first mating part 333a and the second mating part 333b are pin holes that mate with the pin. The servo electric cylinder can precisely control the extension and retraction stroke of the pin, ensuring the reliability of locking and unlocking actions. The size of the pin hole is configured to be slightly larger than the cross-sectional size of the pin to match the relative positional change between the pin and the pin hole when the preceding fuselage section climbs relative to the following fuselage section. In this embodiment, the pin hole can specifically be an oblong hole.

[0053] See Figure 9 and Figure 13 In this embodiment, the supporting unit 304 includes support rollers 341 disposed at the bottom rear end of each body section 301, and support members 342 disposed on each body section 301. Specifically, the support members 342 are guide rails disposed on both sides of the conveyor belt of each body section 301, and the aforementioned basic support surface is the guide rail contact surface on the top surface of the subsequent body section. The support rollers 341 are arranged on both sides of the bottom rear end of the body section 301 and roll along the corresponding guide rails of the adjacent subsequent body section. The support rollers 341 are configured to provide rolling support along the guide rails when the body sections 301 are in relative displacement; when the preceding body section is in a locked state, the support rollers 341 support the support members 342 of the subsequent body section, forming a pitch fulcrum for the preceding body section to perform climbing or descending movements relative to the subsequent body section.

[0054] In this embodiment, the support roller 341 is positioned at a predetermined distance from the rear end of the preceding fuselage section along its length. This predetermined distance is determined based on the maximum gradient the preceding fuselage section needs to traverse in actual operation, the length of the preceding fuselage section itself, and the vertical clearance between the rear end of the preceding fuselage section and the following fuselage section. Since the fulcrum is formed by the support roller 341, the closer the support roller 341 is to the rear end, the smaller the vertical offset of the rear end caused by the front end's lifting and lowering; conversely, the farther the support roller 341 is from the rear end, the larger the vertical offset of the rear end caused by the front end's lifting and lowering. By arranging the support roller 341 at an appropriate distance from the rear end of the preceding fuselage section, the vertical offset of the vertically aligned portion of the rear end of the preceding fuselage section and the following fuselage section is limited to a preset range when the front end of the preceding fuselage section experiences significant height changes during climbing or descending movements. This preset range is smaller than the vertical clearance between the vertically aligned portions of the preceding and following fuselage sections. Since the rear offset is always less than the clearance, the rear end of the preceding fuselage section will not touch the following fuselage section in the vertical direction, thus avoiding component interference between adjacent fuselage sections during climbing or descending.

[0055] The principle behind the aforementioned climbing motion is further explained below. In the locked state, the preceding fuselage section is locked to the following fuselage section by the locking mechanism, and the horizontal position of the rear end of the preceding fuselage section relative to the rear fuselage section is fixed. At this time, if the front end of the preceding fuselage section enters the slope area and experiences a height change (such as extending uphill or retracting downhill), a height difference arises between the front end and its rear end. The preceding fuselage section then undergoes pitching motion around the aforementioned pivot point: the height change at the front end is relatively large, but due to the distance constraint of the pivot point near the rear end, the height deviation of the rear end is controlled within a very small range. In other words, this embodiment, through the geometric lever relationship between the pivot point position and the rear end of the fuselage section, transforms the large height change at the front end into a small height deviation at the rear end within the clearance range, ensuring that the rear end of the preceding fuselage section does not contact or interfere with the rear fuselage section. This principle applies to both extending uphill and retracting downhill conditions.

[0056] See Figures 12 to 13 In this embodiment, the multi-section telescopic conveyor with a long span and segmented incline also includes a guide and reset mechanism. The guide and reset mechanism comprises two parts: a side guide 305 and a bottom guide 306, which together complete the reset and alignment after each work cycle. The side guide 305 is responsible for laterally assisting the preceding section in repositioning relative to the following section during the retraction process, while the bottom guide 306 guides the support rollers of the supporting unit to ensure they travel in a straight line, guaranteeing the straightness of the conveyor section's movement.

[0057] See Figure 12 In this embodiment, the side guide portion 305 is disposed between two adjacent fuselage sections 301, specifically including a plurality of side guide wheels 351 disposed on the rear fuselage section. The side guide wheels 351 are arranged at intervals along the extension direction (which may be configured as two rows of guide wheels on both sides of the rear fuselage section in the width direction), and the top of the side guide wheels 351 is configured as a conical structure. In the non-climbing state, when the front fuselage section retracts relative to the rear fuselage section, the conical structure of the side guide wheels 351 fits against the side of the front fuselage section, gradually guiding the front fuselage section to a position aligned with the rear fuselage section in both the height and extension directions. When the front fuselage section performs an extension and climbing action relative to the rear fuselage section, a height difference is generated between the front end and the rear end of the front fuselage section, and the main body of the front fuselage section leaves the guidance range of the side guide wheels 351 and independently performs the climbing action. After the climbing maneuver is completed or during the descent (i.e., the rear end of the preceding fuselage section passes through the slope area and returns to a state roughly level with the following fuselage section), the main body of the preceding fuselage section gradually descends relative to the following fuselage section and enters the guiding range of the side guide wheel 351. The conical structure of the side guide wheel 351 then conforms to the side of the preceding fuselage section again for lateral guidance (guidance in the height direction and guidance in the extension direction).

[0058] See Figure 13 In this embodiment, the bottom guide portion 306 includes guide mating parts 361 disposed on the top surface of each fuselage section 301. The guide mating parts 361 are configured to guide the support rollers 341 of the support unit 304 so that the support rollers 341 travel in a straight line. Specifically, the guide mating parts 361 on the top surface of each fuselage section 301 are guide walls on both sides of the guide rail contact surface of the aforementioned guide rail. The guide walls on both sides cooperate with the support rollers 341 of the previous fuselage section. When the fuselage section tends to deviate due to slight slippage or lateral disturbance during the telescopic movement, the guide walls on both sides limit and constrain the support rollers 341, so that the support rollers 341 always travel in a straight line in the telescopic direction, thereby ensuring the straightness of the movement of each fuselage section, and restoring each fuselage section to the reference position after each operation cycle.

[0059] When the equipment performs the retraction action, the preceding fuselage section is first guided by the conical structure of the side guide wheel 351 of the side guide section 305 to gradually return to its original position from the side (including guidance in the height and extension directions). At the same time, the support rollers 341 of each fuselage section 301 travel in a straight line under the guidance of the guide fitting 361 of the bottom guide section 306. The side guide section 305 and the bottom guide section 306 work together from the side and bottom directions respectively to complete the multi-dimensional guidance of the preceding fuselage section, so that each fuselage section returns to its precise reference position at the end of each operation cycle.

[0060] It should be noted that the above embodiments describe a typical scenario where the sections extend sequentially, starting with the first section. In practical applications, the extension and retraction sequence of each section is not fixed, but can be flexibly adjusted according to the climbing position and the distribution of the transported material. For example, in unloading conditions, when the vehicle is fully loaded, the equipment is at its shortest length. A section at the bottom can be extended and locked first to allow space for unloading. As unloading progresses and the material height decreases, the section at the front can be extended and locked, and then each section can be gradually lengthened to meet operational needs. In loading conditions, the equipment is initially at its longest length. To preserve loading space, a section can be retracted and locked first, and then each section can be gradually shortened. Regardless of the extension / retraction sequence, as long as the section currently traversing the slope is locked and independently climbs using its own supporting unit as a fulcrum during the climbing action—that is, ensuring that only one section is climbing at a time—the core technical effect of large-span segmented climbing can be achieved. Therefore, the extension and retraction sequence of each fuselage section does not constitute a limitation on the present invention, and all of the above scenarios fall within the protection scope of the present invention.

[0061] Example 4 This embodiment further describes the specific implementation methods of the traveling unit of the first section of the multi-section telescopic conveyor equipment in Embodiments 1 and 2, as well as the locking mechanism and reset correction mechanism at the overall machine level. In this embodiment, "front" and "rear" refer to the orientation in the extension direction, consistent with Embodiment 3. In this embodiment, the term "preset initial state" refers to the predetermined position and attitude state achieved by each section relative to the ground and between themselves after all sections have retracted into place, under the action of the reset correction mechanism. The term "support plane" refers to the plane determined by the three contact points between the three ground-feeding traveling components and the ground.

[0062] See Figures 14 to 18 In this embodiment, multiple fuselage sections are sequentially fitted along the telescopic direction and can be relatively displaced along the telescopic direction. The preceding fuselage section in the extension direction of an adjacent fuselage section has a preset extension position relative to the following fuselage section. The first fuselage section 401, one of the multiple fuselage sections, has a walking unit comprising three ground-touching walking components. These three components are configured to form a supporting plane when the first fuselage section 401 touches the ground, ensuring that all three components remain in contact with the ground. Each of the three ground-touching walking components includes two drive wheels 402 and one support wheel 403. The rotation axes of the two drive wheels 402 coincide and are perpendicular to the telescopic direction. The two drive wheels 402 rotate synchronously. The support wheel 403 is located behind the drive wheels 402 in the extension direction, and the distance between the projection of the support wheel 403 and the projections of the two drive wheels 402 in the supporting plane is equal—that is, the support wheel 403 is located on the perpendicular bisector of the two drive wheels 402. The three components form an isosceles triangle. This embodiment utilizes three ground-contacting walking components (two power wheels 402 and one support wheel 403). Using the geometric principle that three points determine a plane (i.e., the support plane), it ensures that all three ground-contacting components maintain full contact with the ground during movement of the first fuselage section 401. This avoids the problem of a wheel suddenly not making sufficient contact with the ground and slipping, causing the first fuselage section 401 to deviate in its direction of travel. (If the first fuselage section 401 has four or more ground-contacting walking components, the ground along the walking path can generally only be guaranteed to be roughly stable and not absolutely flat. Therefore, when encountering slight unevenness, some ground-contacting walking components on the first fuselage section 401 may not make sufficient contact with the ground and slip, causing the first fuselage section 401 to deviate in its direction of travel.) This ensures that the first fuselage section 401 can travel in a straight line along the extension / retraction direction.

[0063] Specifically, the first fuselage section 401 is equipped with a travel driver 404. The output end of the travel driver 404 is connected to a transmission shaft 405 and drives the transmission shaft 405 to rotate. The transmission shaft 405 is perpendicular to the telescopic direction. The transmission shaft 405 is connected to two drive wheels 402, which are configured to be synchronously driven by the transmission shaft 405. The travel driver 404 can be a servo motor or the like (the travel driver 404 and the transmission shaft 405 can be transmitted through a gear set or the like). The rotational power is synchronously transmitted to the two drive wheels 402 through the transmission shaft 405, ensuring that the speed and torque of the two drive wheels 402 are completely consistent. This ensures that the first fuselage section 401 travels in a straight line and avoids deflection caused by inconsistent speeds of the two drive wheels 402.

[0064] In a preferred embodiment, a counterweight unit (not shown in the figure) can be installed on the first section of the fuselage 401. The counterweight unit can be a counterweight block or the like, fixedly installed on the first section of the fuselage 401, and its weight can be set according to actual operational needs. It is used to increase the normal pressure between the two drive wheels 402 and the ground. The addition of the counterweight unit makes the center of gravity of the first section of the fuselage 401 mainly concentrated on the drive wheels 402, increasing the adhesion between the drive wheels 402 and the ground. In scenarios where multi-section telescopic conveyors are climbing or moving on slopes, the possibility of the drive wheels 402 slipping can be effectively reduced.

[0065] In a preferred embodiment, several auxiliary traveling members 406 may also be provided on the first fuselage section 401. These auxiliary traveling members 406 have a gap (e.g., approximately 1 to 2 centimeters) between themselves and the supporting plane, meaning that the auxiliary traveling members 406 do not contact the ground when the first fuselage section 401 is moving normally horizontally. When the first fuselage section 401 tilts due to uneven ground or lateral forces, the auxiliary traveling members 406 contact the ground to provide auxiliary support, limiting the tilting amplitude of the first fuselage section 401 and preventing the equipment from overturning. The auxiliary traveling members 406 may be casters or directional casters, etc. Figure 14 As shown, an auxiliary walking component 406 can be provided on each side of the support wheel 403.

[0066] In a preferred embodiment, a locking mechanism is provided between adjacent fuselage sections (the specific structure of the locking mechanism can be referred to the drive unit 331, locking member 332, first mating part 333a, and second mating part 333b in Embodiment 3). The locking mechanism is configured such that after any fuselage section extends to a preset extension position and is tensioned to a straight state, it locks the fuselage section adjacent to the next fuselage section in the extension direction, so that the locked fuselage section acts as a rigid tension transmission member to drive the adjacent next fuselage section to continue to extend. In this way, each fuselage section is selectively tensioned and straightened one by one and locked in a preset relative position. The power wheel 402 on the first fuselage section 401 drives the locked fuselage sections to synchronously perform extension or retraction actions. That is, the first fuselage section 401 extends relative to the adjacent rear fuselage section until it extends to a preset extension position (i.e., fully extended) and is tensioned to a straight state (the first fuselage section 401 is ensured to travel in a straight line along the extension direction by three ground-mounted walking parts. When the first fuselage section 401 extends to the preset position relative to the rear fuselage section, the first fuselage section 401 and the rear fuselage section are tensioned and both are kept in a straight line along the extension direction). Then it is locked by the locking mechanism. The first fuselage section 401 locked by the locking mechanism and the rear fuselage section become a whole. When the power wheel 402 on the first fuselage section 401 rotates, it drives this whole forward along the extension direction. When the fuselage section at the end of the whole extends to the preset extension position relative to the rear fuselage section and is tensioned to a straight state, the two are locked by the locking mechanism to become a new whole. This process is repeated so that each fuselage section is selectively tensioned and straightened one by one and locked in a preset relative position. This segmented, section-by-section extension method is fundamentally different from the traditional overall synchronous stretching method: in the traditional method, each section of the fuselage extends outwards simultaneously, and the middle section is prone to bending and shifting when it is not tightened; however, this embodiment adopts a segmented tensioning method of "stretching the next section after straightening one section", so that each section has reached a straight tension state before locking, and after locking, it acts as a rigid component to transmit tension, which fundamentally ensures the straightness of the multi-section fuselage after unfolding, thereby ensuring the straightness of the conveyor track.

[0067] When the multi-section fuselage performs a retraction action, the locking mechanisms between adjacent fuselage sections unlock sequentially from back to front along the extension direction. The reset and correction mechanism is configured to guide the unlocked fuselage sections sequentially during the retraction action so that the multi-section fuselage reaches a preset initial state when it retracts into place. The reset and correction mechanism in this embodiment includes a ground guide and a fuselage guide. The ground guide and fuselage guide are in a cooperative relationship with the side guide 305 and bottom guide 306 in Embodiment 3—the side guide 305 and bottom guide 306 in Embodiment 3 mainly function as lateral guides between adjacent fuselage sections and guides the movement of the support rollers, while the ground guide and fuselage guide in this embodiment provide retraction and reset guidance at the overall telescopic level.

[0068] See Figure 18 In this embodiment, the ground guide section includes a guide rail 407 laid on the ground along the telescopic direction and guide fittings disposed at the bottom of each fuselage section. The guide fittings are configured to sequentially enter the guide rail 407 when the multiple fuselage sections perform a retraction action, thereby forcibly guiding and resetting each fuselage section through the guide rail 407 so that the multiple fuselage sections reach a preset initial state when retracted into place. Specifically, the guide fittings may be guide wheel units disposed at the bottom of each fuselage section, and the guide wheel unit includes at least one ground rail guide wheel 408 adapted to the guide rail 407. The guide wheel unit may include two symmetrically arranged ground rail guide wheels 408, and when the guide fittings enter the guide rail 407, the two ground rail guide wheels 408 respectively enter the guide channels on both sides of the guide rail 407.

[0069] When the multi-section telescopic conveyor extends, the two ground guide wheels 408 on the guide assembly of the body section first follow the guide rail 407 before leaving it. The guide rail 407 constrains the extension trajectory of the multi-section body section, further ensuring that the body runs in a straight line. Since the guide rail 407 is relatively fixed in position with the ground, the reset reference is completely consistent for each work cycle. The cumulative positional deviation generated during the extension and travel processes of the multi-section telescopic conveyor is cleared to zero during the retraction reset, so that the next travel starts from the same reference, thereby ensuring the stability of the travel accuracy of the multi-section telescopic conveyor throughout its entire life cycle.

[0070] See Figure 17The fuselage guide is located on the top of each fuselage segment except for the first fuselage segment 401. It should be noted that the fuselage guide may or may not be located on the first fuselage segment 401; this application does not impose any limitation on this. The fuselage guide includes several side guide wheels (the specific structure of the side guide wheels can be referred to as the side guide wheel 351 in Embodiment 3, and the top can be a conical structure). The side guide wheels are configured to guide the preceding fuselage segment from the side of the preceding fuselage segment during the retraction process of the multiple fuselage segments, after any fuselage segment unlocks from the preceding fuselage segment adjacent to it in the extension direction, so that the multiple fuselage segments reach a preset initial state when retracted into place, further ensuring that each fuselage segment is precisely aligned when retracted into place.

[0071] Specifically, in the preset initial state of the multi-section fuselage, the fuselage guide section on any fuselage section includes side guide wheels located on both sides of the preceding fuselage section in the extension direction, and the side guide wheels on the same side of the preceding fuselage section are arranged along the extension direction. The side guide wheels on both sides of the same fuselage section are symmetrically arranged; the span between the first and last side guide wheels on the same fuselage section along the extension direction is configured such that the angular deviation of the preceding fuselage section between the first and last side guide wheels when the preceding fuselage section retracts into place in the extension direction is limited to a preset tolerance range. The larger the span, the smaller the angular deviation produced under the same offset—for example, the span can reach several meters, and even if there is a lateral offset of several millimeters in the preceding fuselage section, the angular deviation produced under a long span is extremely small, thereby ensuring high precision of lateral guidance.

[0072] The retraction mechanism operates as follows: each fuselage section is locked by a locking mechanism. The drive wheel 402 on the first fuselage section 401 rotates to drive the entire multi-section fuselage to move towards the guide rail 407. The ground rail guide wheel 408 on the last fuselage section in the extension direction enters the guide rail 407 first, until the last fuselage section moves into place (and is restricted from moving further). At this time, the ground rail guide wheels 408 on multiple fuselage sections may have already entered the guide rail 407. Then, the locking mechanism between the last fuselage section and its preceding fuselage section is unlocked, and the preceding fuselage section retracts relative to the last fuselage section. During the retraction process, the preceding fuselage section is guided by the side guide wheel on the last fuselage section. After the preceding fuselage section retracts into place relative to the last fuselage section, the locking mechanism between the preceding fuselage section and its adjacent preceding fuselage section is unlocked. The above process is repeated until all fuselage sections retract into place. The ground guide and fuselage guide work together from the bottom and sides to ensure that all fuselage sections are accurately restored to their preset initial state when they retract into place.

[0073] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited to the above embodiments. Even if various changes are made to the present invention, if these changes fall within the scope of the claims of the present invention and their equivalents, they shall still fall within the protection scope of the present invention.

Claims

1. A ramp conveying mechanism for a conveying device, characterized in that, The conveying equipment includes multiple body sections arranged in sequence. Each body section is equipped with a conveyor belt driven by a conveyor roller. The conveyor roller is driven to rotate by a corresponding power source. The inclined conveying mechanism is arranged between adjacent body sections. The multiple body sections include a feeding body section and at least one transport body section. The inclined conveying mechanism includes: A front roller is disposed on the front side of the corresponding conveyor body section in the conveying direction via a gap maintaining unit. The diameter of the front roller is smaller than the diameter of the conveying roller of the corresponding conveyor body section. The gap maintaining unit is configured to maintain a preset distance between the front roller and the conveyor belt of the preceding body section. The front roller is configured to receive driving force from the power source corresponding to the transport body section and rotate actively to lift part of the conveyed material from the conveyor belt of the previous body section through friction, forming a first-stage climbing action; and the front roller is configured to cooperate with the conveyor belt of the previous body section and the conveyor belt of the corresponding transport body section to continue to move the conveyed material to the corresponding transport body section, forming a second-stage climbing action.

2. The inclined conveying mechanism of the conveying equipment as described in claim 1, characterized in that, The outer ring surface of the front roller is provided with a lifting structure, which is configured to contact the conveyed material and lift the conveyed material upward by friction.

3. The inclined conveying mechanism of the conveying equipment as described in claim 2, characterized in that, The lifting structure includes a plurality of teeth arranged circumferentially on the outer ring surface of the front roller. Each tooth is configured to sequentially enter the contact area between the surface of the conveyed material and the front roller when the front roller rotates, so as to lift the conveyed material upward by friction and drive it along the conveying direction.

4. The inclined conveying mechanism of the conveying equipment as described in claim 3, characterized in that, The toothed portion includes a front tooth surface located in front of the rotation direction of the front roller and a rear tooth surface located behind it. The rear tooth surface is configured to be inclined along the tooth root to the tooth tip toward the rotation direction of the front roller.

5. The inclined conveying mechanism of the conveying equipment as described in claim 4, characterized in that, The plane containing the front tooth surface coincides with the rotation axis of the front roller.

6. The inclined conveying mechanism of the conveying equipment as described in claim 1, characterized in that, The gap maintaining unit includes two support members arranged at intervals. The first ends of the two support members are rotatably connected to the corresponding conveyor body section, and the second ends of the two support members are respectively supported on both sides of the preceding body section in the width direction of the conveyor belt; wherein, the front roller is rotatably connected between the two support members.

7. The inclined conveying mechanism of the conveying equipment as described in claim 6, characterized in that, The gap maintaining unit further includes a support wheel installed at the second end of the support member, the support wheel being configured to roll and support the front fuselage section; The front roller is configured to maintain a constant preset distance between itself and the conveyor belt of the preceding section by means of the rolling support of the support wheel and the swing of the support relative to the corresponding transport section.

8. The inclined conveying mechanism of the conveying equipment as described in claim 1, characterized in that, The elevation gain of the first stage of climbing is A, the elevation gain of the second stage of climbing is B, and the ratio of A to B ranges from 0.3 to 0.

7.

9. The inclined conveying mechanism of the conveying equipment as described in claim 1, characterized in that, The diameter of the front roller is selected such that the preset spacing is less than the minimum size of the material being transported, so that the material being transported can transition from the conveyor belt of the previous section of the machine body to the conveyor belt of the corresponding transport section via the front roller.

10. A multi-section telescopic conveyor, characterized in that, Including the inclined conveying mechanism of the conveying equipment as described in any one of claims 1 to 9.

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