Automatic clutch with split belt pulley

Abstract

The utility model relates to the technical field of mechanical transmission, in particular to an automatic clutch with a split belt pulley. Comprising a driving shaft, a belt pulley installed on the driving shaft and a transmission belt installed on the belt pulley, the belt pulley comprises a first wheel flange and a second wheel flange, the first wheel flange is installed on the driving shaft in an axial moving mode through a spline, and a first throwing block and a second throwing block which are used for pushing the first wheel flange to move in the axial direction are arranged on the outer side of the first wheel flange. The first flail block and the second flail block are sleeved on the driving shaft through the long holes, the inner side surfaces of the first flail block and the second flail block are inclined surfaces inclined to the axis of the driving shaft, and a first spring is arranged between the first flail block and the second flail block; a second spring used for keeping the spacing distance between the first wheel flange and the second wheel flange is arranged between the first wheel flange and the second wheel flange. Clutch is achieved by changing the width of the belt wheel groove, centrifugal force generated when power equipment rotates is used for driving the throwing block to move, the distance between the first wheel flange and the second wheel flange is changed, clutch is automatically controlled through rotating speed changes of the power equipment, manual operation is not needed, and the automation degree is high; and the belt can be prevented from being abraded when the clutch is separated.

Description

Technical Field

[0001] This utility model relates to the technical field of mechanical transmission, specifically to an automatic clutch with a split-type pulley. Background Technology

[0002] Belt drive, also known as belt transmission, is a type of mechanical transmission. It consists of one or more belts tightly fitted onto two pulleys. The two pulleys are mounted on the drive shaft and the driven shaft, respectively. Motion and power are transmitted using the friction between the belt and the two pulleys. Belt rotation can be used for long-distance transmission between the two shafts of a working machine and a power machine. Because belts are elastic, they can dampen impacts, reduce vibration, and provide smooth transmission. Belt drives are simple to implement, low in cost, easy to maintain, and easy to replace. In existing belt drive devices, the pulley groove width is fixed, and a fixed-width belt is used to transmit power. A pressure pulley or tensioner pulley acts as a clutch mechanism to control the power output. For example, Chinese Patent 2016213450311 discloses "A Roller-Tightening Belt Clutch Mechanism for a Turning Machine", publication number CN206751680U. The key technical point of the solution is to set up a cylinder bracket, a roller bracket, and a driven pulley bracket on the main frame. A piston-type actuator is hinged on the cylinder bracket, and a V-belt tensioning roller bracket is hinged on the roller bracket. The piston rod of the piston-type actuator is hinged on the V-belt tensioning roller bracket. The V-belt tensioning roller on the swinging V-belt tensioning roller bracket presses the V-belt between the driving pulley and the driven pulley. However, this type of tensioner clutch mechanism has certain hidden dangers. Because the pulley itself has a certain tension, sometimes the belt cannot completely disengage from the pulley groove after the pressure pulley or tensioner is released. Common pulley grooves are trapezoidal structures that are wider on the outside and narrower on the inside. If the belt cannot completely disengage from the pulley groove, it will become more deeply stuck in the pulley groove as the pulley rotates and rotate with the pulley. In addition, in order to prevent the belt from disengaging from the pulley groove after the tensioner is released, the clearance between the master and slave pulleys and the belt cannot be too large. Otherwise, if the belt falls out of the pulley groove, the machine needs to be stopped and the belt manually reset. However, if the clearance between the belt and the pulley is too small, incomplete disengagement is likely to occur. My other Chinese patent, 2023228019516, authorized publication number CN220816445U, discloses a "Clutch Mechanism for Belt Drive in Small Agricultural Machinery." This mechanism uses a split-type pulley structure, including a first rim with an axle and a second rim slidably mounted on the outer end of the axle. The belt clamping surfaces of the first and second rims are opposite each other. A release bearing assembly for axial movement of the second rim is provided on its outer side. The release bearing assembly includes a bearing seat on the outer side of the second rim and a mounting seat on the outer side of the bearing seat. A bearing is installed in the bearing seat, and a tooth is provided on the outer side of the bearing seat facing the mounting seat. A pull rod is fixedly connected to the side wall of the bearing seat, and a tooth adapter matching the tooth is provided on the side of the mounting seat facing the bearing seat. This clutch mechanism achieves engagement or disengagement of the transmission mechanism by changing the width of the pulley groove to clamp or loosen the belt, completely eliminating the problem of incomplete disengagement in tension wheel clutch mechanisms. It has good engagement and disengagement effects, and the belt does not stick after disengagement.However, this clutch mechanism can only be manually disengaged to move the first or second wheel rim axially, which is relatively complex to operate and has a low degree of automation. Summary of the Invention

[0003] This invention provides an automatic clutch with a split pulley that is simple to operate and highly automated in order to solve the above problems.

[0004] The technical solution adopted by this utility model to solve the technical problem is:

[0005] The automatic clutch with a split pulley of this utility model includes a drive shaft, a pulley mounted on the drive shaft, and a transmission belt mounted on the pulley. The pulley includes a first rim and a second rim with belt clamping surfaces facing each other. The first rim is axially movable on the drive shaft via a spline. A first and a second sling block are provided on the outer side of the first rim for pushing the first rim to move axially. Both the first and second sling blocks are fitted onto the drive shaft through elongated holes. The outer surfaces of the first and second sling blocks are vertical planes perpendicular to the axis of the drive shaft, and the inner surfaces of the first and second sling blocks are inclined planes inclined to the axis of the drive shaft. The inner surfaces of the first and second sling blocks are in contact with each other. A first spring is installed between the first and second sling blocks. A bearing for supporting the inner annular surface of the transmission belt is provided between the first and second rims. A second spring for maintaining the distance between the first and second rims is provided between the first and second rims.

[0006] This solution utilizes centrifugal force to drive the moving blocks and change the distance between the first and second wheel rims to achieve clutch engagement. It is simple to operate, highly automated, and can avoid belt wear when the clutch disengages.

[0007] Preferably, the inclined surfaces of the first and second throwing blocks are provided with mutually fitting inclined grooves and inclined sliders, the outer end of the first throwing block is provided with a first counterweight, the outer end of the second throwing block is provided with a second counterweight, and the two ends of the first spring are respectively connected to the first counterweight and the second counterweight.

[0008] With this scheme, the first and second throwing blocks can slide relative to each other along the inclined plane, thereby changing the distance between the vertical surfaces of the two throwing blocks.

[0009] Preferably, the drive shaft includes a shaft connected to a power machine, a spline sleeve fixedly fitted on the front section of the shaft, a first and a second sling block fitted on the rear section of the shaft through an elongated hole, and the first and second rims being axially movable on the spline sleeve via splines. A flat washer is provided at the outer end of the spline sleeve, and the center of the flat washer is fixedly connected to the end of the shaft by bolts.

[0010] This solution allows for convenient production, processing, and assembly of the split drive shaft.

[0011] Preferably, a sliding groove for accommodating the first and second throwing blocks is provided on the outer side of the first wheel rim; an annular boss is provided on the inner side of the first wheel rim facing the second wheel rim, and the bearing is mounted on the boss.

[0012] With this solution, the block-throwing chute can limit the block-throwing to rotate with the first wheel rim while allowing it to move radially along the length of the block-throwing chute.

[0013] Preferably, a spring seat is provided on the inner side of the second wheel rim facing the first wheel rim, and one end of the second spring is installed in the spring seat and the other end is connected to the end face of the boss.

[0014] This solution allows the spring seat to fix the position of the second spring, preventing it from falling off.

[0015] Preferably, an intermediate rim is provided between the first rim and the second rim, and the bearing for supporting the inner ring surface of the transmission belt includes a first bearing disposed between the intermediate rim and the first rim and a second bearing disposed between the intermediate rim and the second rim; the second spring for maintaining the distance between the first rim and the second rim includes a rear end second spring disposed between the intermediate rim and the first rim and a front end second spring disposed between the intermediate rim and the second rim.

[0016] With this design, the intermediate rim, the first rim, and the second rim together form a double-groove pulley with variable groove width.

[0017] Preferably, the first bearing is embedded in the inner side of the first rim, the second bearing is embedded in the inner side of the second rim, and spring seats for mounting the rear second spring and the front second spring are respectively provided on both sides of the intermediate rim.

[0018] With this solution, the first and second bearings can reduce wear on the inner ring surface of the belt, and the spring seat can fix the position of the rear and front second springs to prevent the springs from falling off.

[0019] Preferably, a mounting plate is fixedly connected to the rear end of the drive shaft, and the mounting plate is provided with mounting holes, with multiple mounting holes evenly distributed around the drive shaft.

[0020] This solution allows for easy connection of the mounting plate to the flywheel of the power unit, transmitting power to the drive shaft.

[0021] Preferably, the rear end of the shaft is fixedly connected to an equilateral triangular disk-shaped mounting plate, and each of the three vertices of the mounting plate is provided with a mounting hole. A pad is provided on the outer side of the mounting plate at the position corresponding to the mounting hole.

[0022] This solution allows for easy connection of the mounting plate to the flywheel of a power unit such as a water-cooled diesel engine, transmitting power to the drive shaft.

[0023] Because of the above structure, the clutch achieves engagement by changing the width of the pulley groove. It uses the centrifugal force of the rotating power equipment to drive the moving block and change the distance between the first and second wheel rims. The clutch engagement is automatically controlled by the speed change of the power equipment, eliminating the need for manual operation, resulting in a high degree of automation, and avoiding wear on the belt when the clutch disengages. Attached Figure Description

[0024] Figure 1 This is a cross-sectional structural diagram of the clutch in the disengaged state according to an embodiment of the present invention.

[0025] Figure 2 yes Figure 1 A schematic diagram of the assembly structure of the embodiment.

[0026] Figure 3 yes Figure 1 A cross-sectional structural diagram of the clutch in the engagement state of the embodiment.

[0027] Figure 4 A three-dimensional structural diagram showing the interaction between the first and second throwing blocks.

[0028] Figure 5 This is a three-dimensional structural diagram of the first rim.

[0029] Figure 6 This is a schematic diagram of the three-dimensional structure of the second rim.

[0030] Figure 7 This is a three-dimensional structural diagram of a shaft with a mounting plate in another embodiment.

[0031] Figure 8 This is a cross-sectional structural schematic diagram of another embodiment of the present invention. Detailed Implementation

[0032] The present invention will be further described in detail below with reference to the accompanying drawings. Identical components are indicated by the same reference numerals. It should be noted that the terms "front," "rear," "left," "right," "upper," and "lower" used in the following description refer to directions in the drawings, and the terms "bottom surface," "top surface," "inner," and "outer" refer to directions away from the geometric center of a specific component.

[0033] like Figure 1 , Figure 2 As shown, the automatic clutch with a split pulley of this utility model includes a drive shaft, a pulley mounted on the drive shaft, and a transmission belt mounted on the pulley. This embodiment uses a single-groove pulley, and only one transmission belt can be installed on the pulley. The transmission belt is a V-belt with a trapezoidal cross-section. V-belt transmission relies on the friction generated by the two sides of the V-belt pressing against the sides of the pulley groove to transmit power. V-belts are more compact than flat belts, and since they are seamless transmission belts, the transmission is smoother, making them the most widely used type of belt drive. The pulley includes a first rim 2 and a second rim 5 with belt clamping surfaces facing each other. Both the first rim 2 and the second rim 5 are disc-shaped structures, with annular and inclined belt clamping surfaces on their inner edges. The inclination angle of the belt clamping surfaces is adapted to the inclination angle of the transmission belt sides, so that the sides of the transmission belt can precisely fit against the belt clamping surfaces of the first rim 2 or the second rim 5. The gap between the first rim 2 and the second rim 5 relative to the belt clamping surface forms a groove 52 for mounting the drive belt. The cross-section of the groove 52 is trapezoidal, and its width depends on the distance between the first rim 2 and the second rim 5. Figure 1 As shown, when the distance between the first rim 2 and the second rim 5 is greater than the width of the drive belt, the pulley cannot drive the drive belt, and the clutch is in a disengaged state; Figure 3 As shown, when the first wheel rim 2 or the second wheel rim 5 moves relative to each other and the width of the wheel groove 52 decreases to less than the width of the transmission belt, the two belt clamping surfaces of the first wheel rim 2 and the second wheel rim 5 clamp the transmission belt, causing the transmission belt to rotate with the pulley. At this time, the clutch is in the engaged state.

[0034] like Figure 1 , Figure 2 As shown, the first rim 2 is axially movable on the drive shaft via a spline, allowing the first rim 2 to rotate with the drive shaft while also being axially movable on the drive shaft. At this time, the second rim 5, which cooperates with the first rim 2, can be either fixedly mounted on the drive shaft or mounted on the drive shaft via a spline.

[0035] The outer side of the first wheel rim 2 is provided with a first throwing block 6 and a second throwing block 7 for pushing the first wheel rim 2 to move axially. The first throwing block 6 and the second throwing block 7 are symmetrically distributed around the axis of the drive shaft to generate centrifugal forces in opposite directions during rotation. The outer surface of the first wheel rim 2 is provided with a throwing block groove 21 to accommodate the first throwing block 6 and the second throwing block 7, such as... Figure 5As shown, the first swing block 6 and the second swing block 7 are located in the swing block groove 21 and can slide along the length direction of the swing block groove 21. Additionally, an annular protective cover 23 can be provided at the edge of the outer side of the first wheel rim 2 of the disc-shaped structure. This protective cover 23 houses the first swing block 6 and the second swing block 7, preventing debris and dust from affecting the flexibility of movement. Both the first swing block 6 and the second swing block 7 are fitted onto the drive shaft through elongated holes. Both the first swing block 6 and the second swing block 7 are strip-shaped structures. The elongated holes are located at the inner ends of the first swing block 6 and the second swing block 7, and the width of the elongated holes is adapted to the diameter of the drive shaft, allowing the drive shaft to pass through. The length direction of the elongated holes is consistent with the length direction of the first swing block 6 or the second swing block 7. A first counterweight 62 is provided at the outer end of the first swing block 6, and a second counterweight 72 is provided at the outer end of the second swing block 7.

[0036] like Figure 2 , Figure 3 As shown, the outer surfaces of the first swing block 6 and the second swing block 7 are both vertical planes perpendicular to the drive shaft axis, and the inner surfaces of the first swing block 6 and the second swing block 7 are inclined planes inclined to the drive shaft axis, making their inner ends thicker and their outer ends thinner. After the first swing block 6 and the second swing block 7 are assembled onto the drive shaft with their inner surfaces facing each other, their inner surfaces fit together. When the first swing block 6 and the second swing block 7 slide inward, the distance between the outer vertical plane of the first swing block 6 and the outer vertical plane of the second swing block 7 is small, that is, the overall thickness of the first swing block 6 and the second swing block 7 combined is small. Conversely, when the first swing block 6 and the second swing block 7 slide outward along their inner inclined planes, the distance between the outer vertical plane of the first swing block 6 and the outer vertical plane of the second swing block 7 is large, that is, the overall thickness of the first swing block 6 and the second swing block 7 combined is large.

[0037] In addition, a bearing 8 is provided between the first rim 2 and the second rim 5 to support the inner ring surface of the transmission belt. The thickness of the bearing 8 is adapted to the width of the inner ring surface of the transmission belt, and the outer ring surface of the bearing 8 forms the bottom of the groove 52. A circular boss 22 is provided on the inner side of the first rim 2 facing the second rim 5. The boss 22 is concentrically arranged with the first rim 2 and the drive shaft. The bearing 8 is mounted on the boss 22, and the inner ring surface of the bearing 8 is interference-fitted onto the outer ring surface of the boss 22. In use, the inner ring surface of the transmission belt is in contact with the outer ring surface of the bearing 8, so that the outer ring surface of the bearing 8 always rotates with the transmission belt, which can avoid wear of the transmission belt caused by friction between the transmission belt and the pulley when the clutch is disengaged.

[0038] A first spring 16 is installed between the first throwing block 6 and the second throwing block 7. In this embodiment, the first spring 16 is a tension spring, which is used to pull the first throwing block 6 and the second throwing block 7 inward to minimize the distance between the outer vertical surface of the first throwing block 6 and the outer vertical surface of the second throwing block 7. No thrust is applied to the first wheel flange 2, and the initial state of the clutch is the disengaged state.

[0039] A second spring 14 is provided between the first rim 2 and the second rim 5 to maintain the distance between them. Figure 1 , Figure 2 In this embodiment, the second spring 14 is a compression spring. When not subjected to other external forces, the second spring 14 pushes the first rim 2 away from the second rim 5. At this time, the width of the pulley groove is greater than the width of the transmission belt, and the transmission belt does not rotate with the pulley. The initial state of the clutch is the disengaged state. When the first rim 2 is subjected to external force and moves toward the second rim 5, the second spring 14 is compressed, and the width of the pulley groove 52 decreases until the belt clamping surfaces of the first rim 2 and the second rim 5 clamp the transmission belt from both sides. At this time, the transmission belt rotates with the pulley, and the state of the clutch changes to the engaged state.

[0040] like Figure 4 As shown, the inclined surfaces of the second throwing block 7 and the first throwing block 6 are provided with mutually engaging inclined grooves 71 and inclined sliders 61. The inclined groove 71 is a strip-shaped groove arranged along the length direction of the second throwing block 7, and the inclined slider 61 is a protrusion that fits into the inclined groove 71. Thus, when the inclined surfaces of the first throwing block 6 and the second throwing block 7 are in contact, the first throwing block 6 and the second throwing block 7 can only slide relative to each other along their length, and cannot slide laterally. Of course, as another embodiment of this utility model, the inclined groove can also be set on the inclined surface of the first throwing block 6, and the inclined slider can be set on the inclined surface of the second throwing block 7, as long as the direction of relative sliding between the two can be limited. The two ends of the first spring 16 are respectively connected to the first counterweight 62 and the second counterweight 72. Figure 2 As shown, a pin for mounting a first spring 16 is provided on each side of the first counterweight 62 and the second counterweight 72. The two first springs 16 are located on both sides of the first swing block 6 and the second swing block 7, respectively, and the two ends of the first springs 16 are hooked onto the corresponding pins. The pins can be shaft-shaped protrusions integrally set on the side of the first counterweight 62 or the second counterweight 72, or they can be screws or bolt-like components that are threaded to the side of the first counterweight 62 or the second counterweight 72.

[0041] like Figure 1 , Figure 2 , Figure 7As shown, the drive shaft includes a shaft 41 connected to the power machinery and a spline sleeve 4 fixedly fitted onto the front section of the shaft 41. The shaft 41, in its length direction, can be divided into a front section for mounting the spline sleeve 4 and a rear section for mounting the first counterweight 62 and the second counterweight 72. A shaft keyway 411 is provided on the side wall of the front section of the shaft 41, and a corresponding matching keyway 412 is provided on the inner wall of the spline sleeve 4. The spline sleeve 4 is fitted onto the front end of the shaft 41. By aligning the shaft keyway 411 with the keyway 412 on the inner wall of the spline sleeve 4, and installing a key in the keyway, the spline sleeve 4 can be locked onto the shaft 41. The outer wall of the spline sleeve 4 is provided with a spline groove, and the mounting holes in the center of the first rim 2 and the second rim 5 are provided with matching splines 53. By aligning the splines 53 on the mounting holes of the first rim 2 and the second rim 5 with the spline groove on the spline sleeve 4 and fitting them onto the spline sleeve 4, the first rim 2 and the second rim 5 can be fixed and rotate with the spline sleeve 4, and at the same time can move axially on the spline sleeve 4.

[0042] The rear section of the shaft 41 is a smooth shaft. The first and second sling blocks 6 and 7 are fitted onto the rear end of the shaft 41 through elongated holes. The first and second rims 2 and 5 are axially movable on the spline sleeve 4 at the front section of the shaft 41 via splines. A flat washer 11 is provided at the outer end of the spline sleeve 4. The diameter of the flat washer 11 is larger than the maximum inner diameter of the spline sleeve 4, which can prevent the spline sleeve 4 from falling off. The center of the flat washer 11 is fixedly connected to the end of the shaft 41 by bolts 10.

[0043] Of course, the spline sleeve 4 can also be fixedly connected to the shaft 41 by welding or other methods, or the drive shaft can be an integrated structure of the spline sleeve 4 and the shaft 41.

[0044] To facilitate the connection between the drive shaft and the power unit, such as Figure 2 As shown, a mounting plate 1 is fixedly connected to the rear end of the drive shaft. The mounting plate 1 is a disc, and the rear end of the drive shaft is fixedly connected to the center of the mounting plate 1. The mounting plate 1 is provided with mounting holes 11, and multiple mounting holes 11 are evenly distributed around the drive shaft. In use, simply align the outer surface of the mounting plate 1 with the outer surface of the flywheel at the output end of the power unit, align the mounting holes 11 on the mounting plate 1 with the mounting holes on the flywheel of the power unit, and insert bolts into the mounting holes and tighten them.

[0045] As another embodiment of this utility model, such as Figure 7 As shown, an equilateral triangular mounting plate 1 is fixedly connected to the rear end of the shaft 41. Each of the three vertices of the mounting plate 1 has a mounting hole 11, and a pad 12 is provided on the outer side of the mounting plate 1 corresponding to the mounting hole 11. This equilateral triangular mounting plate 1 is lightweight and easier to assemble and disassemble.

[0046] As a further improvement of this utility model, a spring seat 51 is provided on the inner side of the second rim 5 facing the first rim 2. Multiple spring seats 51 are evenly distributed around the central axis of the second rim 5. In this embodiment, the spring seat 51 is a circular groove or blind hole with a diameter adapted to the outer diameter of the second spring 14. One end of the second spring 14 is installed in the spring seat 51, and the other end passes through the bearing 8 and abuts against the end face of the boss 22.

[0047] In use, the drive shaft is connected to the flywheel of a power unit such as a diesel engine via a mounting plate. The flywheel drives the drive shaft to rotate, and the drive shaft drives the first wheel rim 2 and the second wheel rim 5, as well as the first swing block 6 and the second swing block 7 to rotate synchronously. Figure 1 As shown, when the power unit is stopped or idling, the drive shaft does not rotate or rotates very slowly. The first and second throwing blocks 6 and 7, under the tension of the first spring 16, are positioned closer to the central axis of the drive shaft. At this time, the drive shaft is located near the end of the elongated hole, and the distance between the outer vertical surfaces of the first throwing block 6 and the second throwing block 7 is minimal. The throwing blocks do not exert any thrust on the first wheel rim 2. Under the action of the second spring 14, the first wheel rim 2 is positioned away from the second wheel rim 5. The width of the groove between the first wheel rim 2 and the second wheel rim 5 is greater than the width of the transmission belt. At this time, the first wheel rim 2 and the second wheel rim 5 are spinning freely, and the clutch is disengaged. When the power unit is working normally, after the speed of the drive shaft increases and exceeds a certain threshold, such as... Figure 3 As shown, the centrifugal force on the first throwing block 6 and the second throwing block 7 is greater than the tension of the first spring 16. The first throwing block 6 and the second throwing block 7 slide outward along the inclined plane on their inner side, so that the drive shaft is located at the far end of the elongated hole. The distance between the vertical plane on the outer side of the first throwing block 6 and the vertical plane on the outer side of the second throwing block 7 increases, and an axial thrust is applied to the first wheel rim 2. This axial thrust overcomes the elastic force of the second spring 14 and pushes the first wheel rim 2 to move towards the second wheel rim 5, so that the width of the groove between the first wheel rim 2 and the second wheel rim 5 decreases and gets stuck on both sides of the transmission belt, driving the transmission belt to rotate. At this time, the clutch is in the engaged state. Once the speed of the power unit drops below a certain threshold, the centrifugal force on the first throwing block 6 and the second throwing block 7 decreases, and the first spring 16 pulls the first throwing block 6 and the second throwing block 7 back to the near end of the drive shaft's central axis. The drive shaft returns to the near end of the elongated hole, the distance between the outer vertical surface of the first throwing block 6 and the outer vertical surface of the second throwing block 7 decreases, and the first wheel rim 2 loses its supporting force. The second spring 14 pushes the first wheel rim 2 away, the wheel groove width increases, the transmission belt is loosened, and the clutch returns to the disengaged state.

[0048] like Figure 8As shown, in another embodiment of this utility model, the pulley can also be a double-groove or multi-groove pulley. In this embodiment, an intermediate rim 3 is provided between the first rim 2 and the second rim 5. Both sides of the intermediate rim 3 are provided with belt clamping surfaces. Adding an intermediate rim 3 between the first rim 2 and the second rim 5 constitutes a double-groove pulley, and adding two intermediate rims 3 constitutes a triple-groove pulley. Figure 8 As shown, taking a clutch with a double-groove pulley as an example, the bearing for supporting the inner annular surface of the transmission belt includes a first bearing 81 disposed between the intermediate rim 3 and the first rim 2, and a second bearing 82 disposed between the intermediate rim 3 and the second rim 5. The first bearing 81 is embedded in the inner side of the first rim 2, and the second bearing 82 is embedded in the inner side of the second rim 5. Both the inner side of the first rim 2 and the inner side of the second rim 5 are provided with annular protrusions for mounting the bearings. The inner annular surface of the first bearing 81 is fitted onto the annular protrusion on the inner side of the first rim 2, and the inner annular surface of the second bearing 82 is fitted onto the annular protrusion on the inner side of the second rim 5.

[0049] In addition, in this embodiment, the second spring for maintaining the distance between the first rim 2 and the second rim 5 includes a rear second spring 141 disposed between the intermediate rim 3 and the first rim 2 and a front second spring 142 disposed between the intermediate rim 3 and the second rim 5.

[0050] To fix the positions of the rear second spring 141 and the front second spring 142, spring seats for mounting the rear second spring 141 and the front second spring 142 are respectively provided on both sides of the intermediate rim 3. The spring seat is a circular groove with a diameter adapted to the outer diameter of the rear second spring 141 or the front second spring 142. One end of the rear second spring 141 or the front second spring 142 is installed in the spring seat, and the other end abuts against the inner side of the first rim 2 or the second rim 5.

[0051] When used with a multi-groove pulley, the working principle of this clutch is the same as that of using a single-groove pulley, and will not be described in detail again.

[0052] While specific embodiments of the present invention have been described in detail above by way of examples, those skilled in the art should understand that the examples are for illustrative purposes only and not intended to limit the scope of the present invention. Those skilled in the art should understand that modifications can be made to the above embodiments without departing from the scope and spirit of the present invention. The scope of the present invention is defined by the appended claims.

Claims

1. An automatic clutch with split pulley, comprising a driving shaft, a pulley mounted on the driving shaft, a transmission belt mounted on the pulley, characterized in that: The pulley comprises a first rim (2) and a second rim (5) oppositely arranged with a belt clamping surface, the first rim (2) is axially movably mounted on a driving shaft through a spline, the outer side of the first rim (2) is provided with a first flinger (6) and a second flinger (7) for pushing the first rim (2) to move axially, the first flinger (6) and the second flinger (7) are both sleeved on the driving shaft through a long hole, the outer side of the first flinger (6) and the second flinger (7) is a vertical surface perpendicular to the axis of the driving shaft, the inner side of the first flinger (6) and the second flinger (7) is an inclined surface inclined to the axis of the driving shaft, and the inner sides of the first flinger (6) and the second flinger (7) are in close contact with each other, and a first spring (16) is mounted between the first flinger (6) and the second flinger (7); the first rim (2) and the second rim (5) are provided with a bearing (8) for bearing the inner ring surface of the transmission belt, and a second spring (14) is arranged between the first rim (2) and the second rim (5) for maintaining the distance therebetween.

2. The automatic clutch with split pulley according to claim 1, characterized in that The inclined surfaces of the first flinger (6) and the second flinger (7) are provided with an inclined surface sliding groove (71) and an inclined surface sliding block (61) in close contact with each other, the outer end of the first flinger (6) is provided with a first counterweight (62), the outer end of the second flinger (7) is provided with a second counterweight (72), and the two ends of the first spring (16) are connected to the first counterweight (62) and the second counterweight (72) respectively.

3. The automatic clutch with split pulley according to claim 1 or 2, characterized in that: The driving shaft comprises a shaft rod (41) connected to a power machine, a spline sleeve (4) fixedly sleeved on the front section of the shaft rod (41), the first flinger (6) and the second flinger (7) are sleeved on the rear section of the shaft rod (41) through a long hole, the first rim (2) and the second rim (5) are axially movably mounted on the spline sleeve (4) through a spline, and the outer end of the spline sleeve (4) is provided with a flat pad (11), the center of the flat pad (11) is fixedly connected to the end of the shaft rod (41) through a bolt (10).

4. The automatic clutch with split pulley according to claim 1 or 2, characterized in that: The outer side of the first rim (2) is provided with a flinger sliding groove (21) for accommodating the first flinger (6) and the second flinger (7); the inner side of the first rim (2) facing the second rim (5) is provided with a circular boss (22), and the bearing (8) is mounted on the boss (22).

5. The automatic clutch with split pulley as set forth in claim 4, characterized in that: The inner side of the second rim (5) facing the first rim (2) is provided with a spring seat (51), one end of the second spring (14) is mounted in the spring seat (51), and the other end is connected to the end surface of the boss (22).

6. The automatic clutch with split pulley according to claim 1 or 2, characterized in that: The first rim (2) and the second rim (5) are provided with an intermediate rim (3), the bearing for bearing the inner ring surface of the transmission belt comprises a first bearing (81) arranged between the intermediate rim (3) and the first rim (2) and a second bearing (82) arranged between the intermediate rim (3) and the second rim (5); the second spring for keeping the interval distance between the first rim (2) and the second rim (5) comprises a rear-end second spring (141) arranged between the intermediate rim (3) and the first rim (2) and a front-end second spring (142) arranged between the intermediate rim (3) and the second rim (5).

7. The automatic clutch with split pulley as set forth in claim 6, characterized in that: The first bearing (81) is embedded in the inner side of the first rim (2), the second bearing (82) is embedded in the inner side of the second rim (5), and the intermediate rim (3) is provided with spring seats for mounting the rear-end second spring (141) and the front-end second spring (142) on the two side surfaces respectively.

8. The automatic clutch with split pulley according to claim 1 or 2, characterized in that: The rear end of the driving shaft is fixedly connected with a mounting disc (1), the mounting disc (1) is provided with mounting holes (11), and a plurality of mounting holes (11) are uniformly distributed around the driving shaft.

9. The automatic clutch with split pulley as set forth in claim 3, characterized in that: The rear end of the shaft rod (41) is fixedly connected with an equilateral triangular disc-shaped mounting disc (1), three mounting holes (11) are arranged on the three vertices of the mounting disc (1) respectively, and the outer side of the mounting disc (1) is provided with a pad (12) corresponding to the positions of the mounting holes (11).

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