An adaptive roller type bi-directional overrunning clutch

Abstract

The present invention relates to an adaptive roller type bidirectional overrunning clutch. The overrunning clutch includes an outer ring, a double star wheel, a central shaft, which are concentrically arranged, as well as a bidirectional yielding key and rollers. The double star wheel includes a first one-way star wheel and a second one-way star wheel with opposite wedge openings and staggered engagement. A plurality of return springs and a plurality of link groups for connecting the first one-way star wheel and the second one-way star wheel are arranged between the first one-way star wheel and the second one-way star wheel. The first one-way star wheel, the second one-way star wheel and the outer ring form an eight-shaped wedge channel arranged circumferentially and uniformly, and the rollers are located in the wedge channel. The bidirectional yielding key is arranged between the first one-way star wheel, the second one-way star wheel and the central shaft. Compared with the prior art, the present invention has the advantages that no additional operating mechanism is required, and it can be automatically engaged or disengaged according to the speed change or the rotation direction change of the main and driven components.

Description

Technical Field

[0001] The present invention relates to the technical field of mechanical transmission systems, and particularly relates to an adaptive roller type bi-directional overrunning clutch. Background Art

[0002] An overrunning clutch is one of the basic components in a mechanical transmission system. It is a clutch that automatically engages or disengages with the change of the speed or the rotation direction of the main and driven components. It is widely used in fields such as packaging machinery, food machinery, light industry machinery, agricultural machinery, metallurgy and mining, petrochemical industry, machine tools, automobiles, weapons, aviation, and power stations.

[0003] According to the working principle, overrunning clutches can be divided into the engagement type and the friction type, among which the engagement type is also called the ratchet type. The ratchet type overrunning clutch has a simple structure, is easy to manufacture, and has high reliability. However, it will produce impact and noise during engagement and is usually suitable for applications with a small speed difference. The friction type overrunning clutch has a smooth engagement without impact and a short idle stroke, can be engaged at any speed, and has a wider application range. Its torque transmission range is from 1 - 100000 Nm.

[0004] The application fields of overrunning clutches include the following three types:

[0005] (1) Speed change: The driven part can obtain two speeds, fast and slow, without disconnecting the motion chain.

[0006] (2) Reverse prevention: A unidirectional overrunning clutch transmits torque in one rotation direction and idles under the action of torque in the opposite direction.

[0007] (3) Intermittent motion: By appropriately combining a bi-directional overrunning clutch and a unidirectional overrunning clutch, intermittent motion of a certain law can be achieved for the driven part.

[0008] However, currently, all bi-directional overrunning clutches in the prior art are controllable types. The controllable overrunning clutch consists of a clutch and a mechanical or electromagnetic switching device, that is, only by manually or automatically switching the staying position of the roller in the wedge-shaped channel from the outside can working modes such as forward or reverse unidirectional overrunning, bi-directional overrunning, and bi-directional wedging be selected. Summary of the Invention

[0009] The purpose of the present invention is to provide an adaptive roller type bi-directional overrunning clutch to overcome at least one of the defects existing in the above-mentioned prior art. This overrunning clutch does not require any additional operating mechanism and can automatically engage or disengage according to the change of the speed or the rotation direction of the main and driven components.

[0010] The purpose of the present invention can be achieved by the following technical solutions:

[0011] An adaptive roller type bi-directional overrunning clutch, which comprises a concentrically arranged outer ring, a double star wheel, a central shaft, as well as a bi-directional yielding key, rollers, ejector rods, springs, etc.;

[0012] The double star wheel mentioned above includes a first one-way star wheel and a second one-way star wheel with opposite wedge openings and staggered engagement. Each one-way star wheel can achieve engagement in one direction and separation in the opposite direction; between the first one-way star wheel and the second one-way star wheel, there are multiple return springs and multiple link groups for connecting the first one-way star wheel and the second one-way star wheel, enabling the two star wheels to rotate relative to each other unidirectionally by a certain angle;

[0013] The first one-way star wheel, the second one-way star wheel and the outer ring form an eight-shaped wedge channel arranged circumferentially and uniformly, and the rollers are located in the wedge channel;

[0014] The bi-directional yielding key is arranged between the first one-way star wheel, the second one-way star wheel and the central shaft.

[0015] Furthermore, one side of the bi-directional yielding key is in rigid contact with the key side walls of the first one-way star wheel and the second one-way star wheel, and there is a space for relative rotation on the other side with respect to the first one-way star wheel and the second one-way star wheel. That is, the first one-way star wheel and the second one-way star wheel are free to move in one side direction, and the movement in the other side direction is restricted.

[0016] Furthermore, the link group includes a first link and a second link; between the first link and the second link, there is a link pin shaft for hinging the first link and the second link; the first one-way star wheel is circumferentially and uniformly provided with a plurality of first link holes connected to the first link; the second one-way star wheel is circumferentially and uniformly provided with a plurality of second link holes connected to the second link.

[0017] Furthermore, a central disk fixedly connected to the central shaft is provided around the central shaft; the central disk is circumferentially and uniformly provided with a plurality of link chutes, and the link pin shaft can slide radially in the link chutes; the link chutes include upper limits and lower limits arranged radially; the distance between the upper limit and the lower limit is the stroke of the link pin shaft; the stroke range must ensure the requirement for the first one-way star wheel and the second one-way star wheel to be disengaged from the wedge, and at the same time prevent the mechanism from having dead points. The central shaft is also circumferentially provided with a third keyway.

[0018] Furthermore, the first one-way star wheel is circumferentially and uniformly provided with a first keyway; the second one-way star wheel is circumferentially and uniformly provided with a second keyway; between the central shaft and the central disk, a third keyway is uniformly provided; the side of the bi-directional yielding key provided with a first yielding clearance groove is inserted into the first keyway; the side of the bi-directional yielding key provided with a second yielding clearance groove is inserted into the second keyway; the first yielding clearance groove and the second yielding clearance groove are arranged in a dislocation and opposite manner on the bi-directional yielding key.

[0019] Furthermore, the wedge-retracting direction of the first one-way star wheel and / or the second one-way star wheel is clockwise, and the notch of the first relief clearance groove and / or the second relief clearance groove is located on the left side of the two-way relief key; the wedge-retracting direction of the first one-way star wheel and / or the second one-way star wheel is counterclockwise, and the notch of the first relief clearance groove and / or the second relief clearance groove is located on the right side of the two-way relief key.

[0020] Furthermore, the width dimensions of the first relief clearance groove and the second relief clearance groove are larger than the moving space for the first one-way star wheel and the second one-way star wheel to disengage from each other. That is to say, the width dimensions of the first relief clearance groove and the second relief clearance groove must satisfy that the first one-way star wheel and the second one-way star wheel have a relative rotational space for disengagement. That is, when the central shaft is active, there is enough relative rotational space between the two star wheels so that the pawls of one star wheel can contact the rollers of the other star wheel and squeeze the rollers into the loose space of the wedge-shaped channel.

[0021] Furthermore, the first one-way star wheel is circumferentially and uniformly provided with first pawls; the second one-way star wheel is circumferentially and uniformly provided with second pawls; the first pawls are inserted into the wedge-shaped channels of the second one-way star wheel and have a gap with the rollers in the wedge-shaped channels; the second pawls are inserted into the wedge-shaped channels of the first one-way star wheel and have a gap with the rollers in the wedge-shaped channels.

[0022] Furthermore, the relationship between the width dimensions of the first relief clearance groove and the second relief clearance groove and the gap δ between the first pawls, the second pawls and the rollers is as follows:

[0023]

[0024] In the formula: Δ is the width dimension of the first relief clearance groove and the second relief clearance groove, δ is the gap between the first pawl or the second pawl and the roller, d is the diameter of the roller, D1 is the inner diameter of the outer ring, and D2 is the diameter of the central shaft.

[0025] Furthermore, the width dimensions of the first relief clearance groove and the second relief clearance groove are related to the upper limit and the lower limit positions of the link chute of the central shaft and cannot interfere with each other.

[0026] Furthermore, the two-way relief key can be replaced by other structures with similar functions and principles.

[0027] Furthermore, the first unidirectional star wheel is circumferentially evenly provided with a plurality of return spring grooves; the second unidirectional star wheel is circumferentially evenly provided with a stopper inserted into the return spring groove; the return spring is installed in the return spring groove, with one end close to the end face of the return spring groove and the other end abutting against the stopper, and through the action of the return spring, the various components of the adaptive roller type two-way overrunning clutch can automatically return to the initial state when the external force is removed.

[0028] Furthermore, the outer ring is an active component, the outer ring rotation speed is greater than or equal to the rotation speed of the central shaft, and the central shaft and the outer ring are automatically bidirectionally engaged; the central shaft is an active component, the central shaft rotation speed is greater than or equal to the rotation speed of the outer ring, and the central shaft and the outer ring are automatically bidirectionally separated.

[0029] Compared with the prior art, the present invention has the following advantages:

[0030] (1) The first one-way star wheel and the second one-way star wheel, the connecting rod group, the central shaft and the connecting rod slot in the present invention are connected to form a working relationship of a six-bar mechanism. With the cooperation of the two-way yield key, the various components of the adaptive roller-type two-way overrunning clutch of the present invention become a coordinated whole. When the outer ring is an active component and the outer ring speed is greater than or equal to the speed of the central shaft, the first one-way star wheel and the second one-way star wheel can support each other and transfer the load, thereby realizing the two-way automatic engagement of the outer ring and the central shaft; when the central shaft is an active component, the connecting rod group can coordinate the motion relationship between the first one-way star wheel and the second one-way star wheel and the central shaft, so that there will be no motion interference between the three, and the first one-way star wheel and the second one-way star wheel can be mutually unwedgeable, thereby realizing the two-way automatic separation of the motion of the outer ring and the central shaft.

[0031] (2) The adaptive roller-type bidirectional overrunning clutch designed in the present invention does not require any additional operating mechanism and can automatically engage or disengage according to the speed change or rotation direction change of the master and slave components.

[0032] (3) The adaptive roller type bidirectional overrunning clutch of the present invention has the technical characteristics of simple structure, reliable operation and wide application range. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 A local anatomical diagram of the adaptive roller type bidirectional overrunning clutch in the embodiment;

[0034] Figure 2 It is a schematic assembly exploded diagram of the adaptive roller type bidirectional overrunning clutch in the embodiment;

[0035] Figure 3 This is a schematic structural diagram of the first unidirectional star wheel in the embodiment;

[0036] Figure 4 is a schematic structural diagram of a second one-way star wheel in an embodiment;

[0037] Figure 5 is a schematic structural diagram of the central shaft in the embodiment;

[0038] Figure 6 is a schematic structural diagram of the two-way relief key in the embodiment;

[0039] Figure 7 is a schematic diagram of the connection relationship and clearance of the connecting rod group in the embodiment;

[0040] As shown in the figure, the reference numerals are as follows: 1 - outer ring; 2 - double star wheel; 3 - central shaft; 4 - two-way relief key; 5 - roller; 21 - first one-way star wheel; 22 - second one-way star wheel; 23 - return spring; 24 - connecting rod group; 211 - first pawl; 212 - first connecting rod hole; 213 - return spring groove; 214 - first key groove; 221 - second pawl; 222 - second connecting rod hole; 223 - stop; 224 - second key groove; 31 - central disc; 32 - third key groove; 33 - connecting rod chute; 35 - upper limit; 36 - lower limit; 41 - first relief clearance groove; 42 - second relief clearance groove; 241 - first connecting rod; 242 - second connecting rod; 243 - connecting rod pin shaft. Detailed implementation manners

[0041] The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments. This embodiment is implemented on the premise of the technical solution of the present invention, and the detailed implementation manners and specific operation processes are given, but the protection scope of the present invention is not limited to the following embodiments.

[0042] Embodiment

[0043] An adaptive roller type two-way overrunning clutch, as Figure 1 shown, is composed of an outer ring 1, a double star wheel 2, a central shaft 3, a two-way relief key 4, a roller 5 and its ejector rod, spring, etc.

[0044] The double star wheel 2 is composed of the first one-way star wheel 21 and the second one-way star wheel 22 with their wedge openings facing each other and being staggeredly engaged, and forms a plurality of circumferentially uniformly arranged eight-shaped wedge channels with the outer ring 1. The first one-way star wheel 21 and the second one-way star wheel 22 are connected by a return spring 23 and a connecting rod group 24, so that the first one-way star wheel 21 and the second one-way star wheel 22 can rotate relative to each other in one direction by a certain angle, as Figure 2 shown. Among them, the first one-way star wheel 21 is circumferentially uniformly provided with a first pawl 211, a first connecting rod hole 212, a return spring groove 213, a first key groove 214, etc., as Figure 3 shown; the second one-way star wheel 22 is circumferentially uniformly provided with a second pawl 221, a second connecting rod hole 222, a stop 223 and a second key groove 224, etc., as Figure 4As shown in the figure. The first pawls 211 of the first one-way star wheel 21 and the second one-way star wheel 22 are inserted into the wedge-shaped channels of the other star wheel respectively, and there is a certain gap with the rollers 5 on the other star wheel. The stopper 223 of the second one-way star wheel 22 is inserted into the reset spring groove 213 of the first one-way star wheel 21. The reset spring 23 is installed in the reset spring grooves 213 evenly arranged circumferentially on the first one-way star wheel 21. One end abuts against the end face of the ring groove 213, and the other end acts on the stopper 223 of the second one-way star wheel 22, so that all components of the self-adaptive roller type bidirectional overrunning clutch can automatically return to the initial state when the external force is removed.

[0045] The connecting rod group 24 of the double star wheel 2 is located between the first one-way star wheel 21 and the second one-way star wheel 22, and on both sides of the central disk 31 of the central shaft 3. The connecting rod group 24 is evenly arranged circumferentially. One connecting rod group 24 includes two connecting rods: the first connecting rod 241 and the second connecting rod 242. The two connecting rods are co-hinged with the pin shaft 243, and the pin shaft 243 is inserted into the connecting rod sliding groove 33 of the central disk 31 of the central shaft 3 and can slide radially along the sliding groove 33, as Figure 7 shown. The first connecting rod 241 is connected to the first connecting rod hole 212 of the first one-way star wheel 21, and the second connecting rod 242 is connected to the second connecting rod hole 222 of the second one-way star wheel 22.

[0046] The central shaft 3 includes a central disk 31, a third key groove 32, a connecting rod sliding groove 33, etc., as Figure 5 shown. The central disk 31 is fixedly connected to the central shaft 3, and a radial connecting rod sliding groove 33 is provided thereon. The connecting rod sliding groove 33 is divided into an upper limit 35 and a lower limit 36. The distance between the upper limit 35 and the lower limit 36 of the connecting rod sliding groove 33 is the stroke of the connecting rod pin 243. The stroke must meet the requirements for the first one-way star wheel 21 and the second one-way star wheel 22 to be disengaged from the wedge, and at the same time prevent the mechanism from having dead points.

[0047] The structure of the bidirectional yielding key 4 is as Figure 6 shown, arranged between the first one-way star wheel 21, the second one-way star wheel 22 and the central shaft 3. One side is in rigid contact with the key side wall of the star wheel, and there is a space for relative rotation on the other side with the star wheel. That is, the movement in one direction of the star wheel is free, and the movement in the other direction is restricted.

[0048] The first yielding clearance groove 41 and the second yielding clearance groove 42 in the upper half of the bidirectional yielding key 4 are arranged in a staggered and opposite manner. Among them, the clearance groove 41 corresponds to the star wheel 21, and 42 corresponds to the star wheel 22; the lower half is embedded in the key groove 33 of the central shaft 3, and the working surface is in close contact with the key wall.

[0049] The notch positions of the relief slots 41 and 42 of the bidirectional relief key 4 are related to the unlocking directions of the corresponding star wheels. Clockwise corresponds to the left, and counterclockwise corresponds to the right. In this embodiment, the wedge-retreating direction of the first one-way star wheel 21 is clockwise. Therefore, the first relief slot 41 of the bidirectional relief key 4 corresponding to the first keyway 214 of the first one-way star wheel 21 is provided on the left side of the bidirectional relief key 4. Similarly, the wedge-retreating direction of the second one-way star wheel 22 is counterclockwise. Therefore, the second relief slot 42 of the bidirectional relief key 4 corresponding to the second keyway 224 of the second one-way star wheel 22 is provided on the right side of the bidirectional relief key 4.

[0050] The width dimensions of the first relief slots 41 and 42 of the bidirectional relief key 4 must satisfy that there is sufficient relative rotation space between the two star wheels, so that the pawls of one star wheel can contact the rollers of the other star wheel and push the rollers into the loose space of the wedge-shaped channel.

[0051] The positional relationships between the first relief slot 41 and the second relief slot 42 of the bidirectional relief key 4 and other components are as Figure 7 shown. The relationship between the width dimensions and the clearance δ between the first pawl 211, the second pawl 221 and the roller 5: In the formula: Δ is the width dimension of the relief slots 41 and 42, δ is the clearance between the first pawl 211 and / or the second pawl 221 and the roller 5, d is the diameter of the roller 5, D1 is the inner diameter of the outer ring 1, and D2 is the diameter of the central shaft 3.

[0052] The width dimensions of the first relief slot 41 and the second relief slot 42 of the bidirectional relief key 4 are related to the upper limit 35 and the lower limit 36 of the connecting rod chute 33 of the central shaft 3 and cannot interfere with each other.

[0053] In this embodiment, the self-adaptive roller type bidirectional overrunning clutch connects the first one-way star wheel 21, the second one-way star wheel 22, the central shaft 3, etc. through the connecting rod group 24 to form the kinematic relationship of a six-bar mechanism, making it an integral whole with coordinated motion.

[0054] The detailed working process of the self-adaptive roller type bidirectional overrunning clutch in this embodiment:

[0055] I. Reset state

[0056] In this embodiment, the self-adaptive roller type bidirectional overrunning clutch enables the components to automatically return to the relative position relationship of the initial state through the circumferentially uniformly arranged reset springs 23:

[0057] (1) The outer ring 1, the first one-way star wheel 21, the second one-way star wheel 22 and the roller 5 remain in contact and are not suspended;

[0058] (2) Within the same wedge-shaped channel, the clearances between the first pawls 211 of the first one-way star wheel 21 and the second one-way star wheel 22, the second pawls 221, and the roller 5 are uniform.

[0059] (3) The first keyways 214 of the first one-way star wheel 21 and the second one-way star wheel 22, the second keyways 224, are in close contact with the non-relieving side of the two-way relieving key 4 without clearance.

[0060] (4) The connecting rod pin shaft 243 of the connecting rod group 24 is at the lower limit 36 of the connecting rod chute 33 of the central shaft 3.

[0061] II. Engaged State

[0062] 1. The outer ring 1 is the driving part, rotating clockwise; the central shaft 3 is the driven part, fixed or the rotational speed of the outer ring is greater than or equal to that of the central shaft.

[0063] The outer ring 1 acts on the roller 5 on the first one-way star wheel 21, causing the roller to slightly move towards the narrow direction of the wedge-shaped channel, and the roller 5 will be wedged tightly; at the same time, the roller 5 on the second one-way star wheel 22 slightly moves towards the loose direction of the wedge-shaped channel, and the roller 5 is in a relaxed state. At this time, due to the first relieving clearance groove 41 between the first one-way star wheel 21 and the two-way relieving key 4, the outer ring 1 will drive the first one-way star wheel 21 to rotate in the same direction; there is no clearance between the non-relieving side of the second one-way star wheel 22 and the two-way relieving key 4, so the second one-way star wheel 22 and the central shaft 3 maintain the same motion state.

[0064] In the kinematic relationship of the six-bar mechanism composed of the first one-way star wheel 21, the second one-way star wheel 22, the first connecting rod 241, the second connecting rod 242, the central shaft 3, and the third keyway 33, the central shaft 3 is relatively fixed, and the second one-way star wheel 22 is also relatively fixed under the action of the two-way relieving key 4. Therefore, the first one-way star wheel 21 can transmit the torque of the outer ring 1 to the central shaft 3 through the following force transmission path: outer ring 1 → roller 5 → first one-way star wheel 21 → first connecting rod 241 → second connecting rod 242 → second one-way star wheel 22 → central shaft 3.

[0065] Thus, the automatic engagement of the central shaft 3 and the outer ring 1 is achieved, and they rotate at the same speed and in the same direction.

[0066] 2. The outer ring 1 is the driving part, rotating counterclockwise; the central shaft 3 is the driven part, fixed or the rotational speed of the outer ring is greater than or equal to that of the central shaft.

[0067] The outer ring 3 acts on the roller 5 on the second one-way star wheel 22, causing the roller 5 to move slightly in the direction of the narrowing of the wedge-shaped channel, and the roller 5 will be wedged tightly; at the same time, the roller 5 on the first one-way star wheel 21 moves slightly in the direction of the relaxation of the wedge-shaped channel, and the roller 5 is in a relaxed state. At this time, due to the second clearance groove 42 between the second one-way star wheel 22 and the two-way yielding key 4, the outer ring 1 will drive the second one-way star wheel 22 to rotate in the same direction; there is no clearance between the non-yielding side of the first one-way star wheel 21 and the two-way yielding key 4, so the first one-way star 21 and the central shaft 3 maintain the same motion state.

[0068] In the kinematic relationship of the six-bar mechanism composed of the first one-way star wheel 21, the second one-way star wheel 22, the first connecting rod 241, the second connecting rod 242, the central shaft 3 and the third keyway 33, the central shaft 3 is relatively fixed, and the second one-way star wheel 22 is also relatively fixed under the action of the two-way yielding key 4. Therefore, the second one-way star wheel 22 can transmit the torque of the outer ring 1 to the central shaft 3 through the following force transmission path: outer ring 1 → roller 5 → second one-way star wheel 22 → second connecting rod 242 → first connecting rod 241 → first one-way star wheel 21 → central shaft 3.

[0069] Thus, the automatic engagement of the central shaft 3 and the outer ring 1 is achieved, and they rotate at the same speed and in the same direction.

[0070] III. Disengaged state

[0071] 1. The central shaft 3 is the driving part, rotating clockwise; the outer ring 1 is the driven part, and the rotational speed of the central shaft 3 is greater than or equal to the rotational speed of the outer ring 1;

[0072] Since there is no clearance between the non-yielding side of the first one-way star wheel 21 and the two-way yielding key 4, the first one-way star wheel 21 will rotate in the same direction as the central shaft 3 and drive the roller 5 on it to move slightly in the direction of the relaxation of the wedge-shaped channel, and the first one-way star wheel 21 will be disengaged from the outer ring 1.

[0073] Due to the second clearance groove 42 between the second one-way star wheel 22 and the two-way yielding key 4, the central shaft 3 cannot drive the second one-way star wheel 22 to move in the same direction, and the roller 5 on the second one-way star wheel 22 will be in a relaxed state.

[0074] When the first pawl 211 on the first one-way star wheel 21 contacts the roller 5 on the second one-way star wheel 22, the roller 5 is pushed into the relaxed space of the wedge-shaped channel, and the second one-way star wheel 22 is disengaged from the outer ring 1.

[0075] 2. The central shaft 3 is the driving part, rotating counterclockwise; the outer ring 1 is the driven part, and the rotational speed of the central shaft 3 is greater than or equal to the rotational speed of the outer ring 1;

[0076] Since there is no clearance between the non-yielding side of the second one-way star wheel 22 and the two-way yielding key 4, the second one-way star wheel 22 will rotate in the same direction as the central shaft 3, and drive the roller 5 thereon to move slightly in the loose direction of the wedge-shaped channel, and the second one-way star wheel 22 will be disengaged from the outer ring 1.

[0077] Due to the first yielding clearance groove 41 between the first one-way star wheel 21 and the two-way yielding key 4, the central shaft 3 cannot drive the first one-way star wheel 21 to move in the same direction, and the roller 5 on the first one-way star wheel 21 will be in a relaxed state.

[0078] When the second pawl 221 on the second one-way star wheel 22 contacts the roller 5 on the first one-way star wheel 21, the roller 5 is pushed into the loose space of the wedge-shaped channel, and the first one-way star wheel 21 is disengaged from the outer ring 1.

[0079] Thus, the two-way automatic separation of the central shaft 3 and the outer ring 1 is achieved.

[0080] In summary, the self-adaptive roller type two-way overrunning clutch of the present invention does not require any additional operating mechanism, and can complete automatic engagement or disengagement according to the speed change or rotation direction change of the main and driven components:

[0081] When the outer ring 1 is the driving part, the rotational speed of the outer ring 1 is greater than or equal to the rotational speed of the central shaft 3, and the central shaft 3 and the outer ring 1 are automatically engaged in two directions.

[0082] When the central shaft 3 is the driving part, the rotational speed of the central shaft 3 is greater than or equal to the rotational speed of the outer ring 1, and the central shaft 3 and the outer ring 1 are automatically separated in two directions.

[0083] The above are only the preferred embodiments of the present invention, and are not intended to limit the present invention in other forms. Any person skilled in the art may use the disclosed technical content to make changes or modifications into equivalent embodiments with equivalent changes. However, any simple modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention without departing from the technical solution content of the present invention still fall within the protection scope of the technical solution of the present invention.

Claims

1. An adaptive roller type bi-directional overrunning clutch, characterized in that, The overrunning clutch includes an outer ring (1), a double star wheel (2), a central shaft (3) arranged concentrically, as well as a bidirectional relief key (4) and rollers (5); The double star wheel (2) includes a first one-way star wheel (21) and a second one-way star wheel (22) with opposite wedge openings and staggered engagement; between the first one-way star wheel (21) and the second one-way star wheel (22), there are a plurality of return springs (23) and a plurality of link groups (24) for connecting the first one-way star wheel (21) and the second one-way star wheel (22); The first one-way star wheel (21), the second one-way star wheel (22) and the outer ring (1) form an eight-shaped wedge channel arranged circumferentially and uniformly, and the rollers (5) are located in the wedge channel; The bidirectional relief key (4) is arranged between the double star wheel (2) and the central shaft (3); The link group (24) includes a first link (241) and a second link (242); between the first link (241) and the second link (242), there is a link pin shaft (243) for hinging the first link (241) and the second link (242); The first one-way star wheel (21) is circumferentially and uniformly provided with a plurality of first link holes (212) connected to the first link (241); the second one-way star wheel (22) is circumferentially and uniformly provided with a plurality of second link holes (222) connected to the second link (242).

2. The self - adaptive roller - type bi - directional overrunning clutch according to claim 1, characterized in that, One side of the bidirectional relief key (4) is in rigid contact with the key side walls of the first one-way star wheel (21) and the second one-way star wheel (22), and the other side has a space for relative rotation with the first one-way star wheel (21) and the second one-way star wheel (22).

3. The self - adaptive roller type bi - directional overrunning clutch according to claim 1, wherein, Around the central shaft (3), there is a central disc (31) fixedly connected to the central shaft (3); The central disc (31) is circumferentially and uniformly provided with a plurality of link chutes (33); the link chutes (33) include an upper limit (35) and a lower limit (36) arranged radially; the distance between the upper limit (35) and the lower limit (36) is the stroke of the link pin shaft (243).

4. An adaptive roller type bi-directional overrunning clutch according to claim 1, wherein, The first one-way star wheel (21) is circumferentially and uniformly provided with a first keyway (214); the second one-way star wheel (22) is circumferentially and uniformly provided with a second keyway (224); The side of the bidirectional relief key (4) provided with a first relief gap groove (41) is inserted into the first keyway (214); the side of the bidirectional relief key (4) provided with a second relief gap groove (42) is inserted into the second keyway (224); the first relief gap groove (41) and the second relief gap groove (42) are arranged in a staggered and opposite manner on the bidirectional relief key (4).

5. An adaptive roller type bi-directional overrunning clutch according to claim 4, characterized in that, When the wedge withdrawal direction of the first one-way star wheel (21) and / or the second one-way star wheel (22) is clockwise, the openings of the first relief gap groove (41) and / or the second relief gap groove (42) are located on the left side of the key of the bidirectional relief key (4); when the wedge withdrawal direction of the first one-way star wheel (21) and / or the second one-way star wheel (22) is counterclockwise, the openings of the first relief gap groove (41) and / or the second relief gap groove (42) are located on the right side of the key of the bidirectional relief key (4).

6. An adaptive roller type bi-directional overrunning clutch according to claim 4, characterized in that, The width dimensions of the first relief clearance groove (41) and the second relief clearance groove (42) are greater than the movement space for the first one-way star wheel (21) and the second one-way star wheel (22) to disengage from each other.

7. An adaptive roller type bi-directional overrunning clutch according to claim 1, characterized in that, The first one-way star wheel (21) is circumferentially and uniformly provided with first pawls (211); the second one-way star wheel (22) is circumferentially and uniformly provided with second pawls (221); The first pawls (211) are inserted into the wedge-shaped channels of the second one-way star wheel (22) and have a clearance with the rollers (5) in the wedge-shaped channels; the second pawls (221) are inserted into the wedge-shaped channels of the first one-way star wheel (21) and have a clearance with the rollers (5) in the wedge-shaped channels.

8. An adaptive roller type bi-directional overrunning clutch according to claim 1, wherein, The first one-way star wheel (21) is circumferentially and uniformly provided with a plurality of return spring grooves (213); the second one-way star wheel (22) is circumferentially and uniformly provided with stoppers (223) inserted into the return spring grooves (213); The return springs (23) are installed in the return spring grooves (213), with one end abutted against the end face of the return spring groove (213) and the other end abutted against the stoppers (223).

9. An adaptive roller type bi-directional overrunning clutch according to claim 1, wherein, The outer ring (1) is the driving component, the rotational speed of the outer ring (1) is greater than or equal to the rotational speed of the central shaft (3), and the central shaft (3) and the outer ring (1) are automatically and bidirectionally engaged; The central shaft (3) is the driving component, the rotational speed of the central shaft (3) is greater than or equal to the rotational speed of the outer ring (1), and the central shaft (3) and the outer ring (1) are automatically and bidirectionally separated.

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