Double-block overrunning clutch

Abstract

The double-block overrunning clutch is a non-contact overrunning clutch with a double-block (3) as a locking element. It does not need to maintain contact with the locking object during the overrunning stroke, which can reduce wear and energy consumption. Since no roller is required to trigger the locking action, a magnetic suspension structure can be used between the rotating parts to further reduce movement resistance and shock absorption. The locking and separation actions of the double-block (3) are directly related to the relative movement direction of the locking object and are not limited by its own speed conditions. The double-block (3) can use a line contact method to perform friction transmission with the locking object, and can also cooperate with a surface contact locking element or a rigid meshing element to greatly improve the load-bearing capacity. In addition, the functions of positive locking and reverse separation, positive separation and reverse locking, and bidirectional locking can be realized through the inclination adjustment mechanism.

Description

Technical Field

[0001] The invention provides an overrunning clutch. Background Art

[0002] Current overrunning clutches are mainly contact roller or wedge overrunning clutches. The roller or wedge must maintain contact with the outer ring or inner ring during the overrunning stroke, which not only generates heat and energy, reducing transmission efficiency, but also causes severe wear and tear, shortening its lifespan. The contactless overrunning clutch overcomes these drawbacks of the contact overrunning clutch and is an important branch of the overrunning clutch. Among them, the wedge-type contactless overrunning clutch has a good development prospect due to its simple structure, reliable locking, and easy separation. However, it also has some defects. During the overrunning stroke, the wedge tilts under the action of centrifugation to maintain the distance from the outer ring and inner ring. This requires a certain speed to achieve, greatly limiting its scope of use. The contact between the wedge and the outer ring and inner ring is line contact, resulting in a small transmission area and easy damage to the transmission surface due to excessive pressure. Summary of the Invention

[0003] The purpose of the present invention is to provide an overrunning clutch device, which uses a double-jointed block (3) as a locking element. It does not need to maintain contact with the locking object during the overrunning stroke, which can reduce wear and energy consumption. Since rollers are not required to trigger the locking action, a magnetic suspension structure can be used between the rotating parts to further reduce movement resistance and shock absorption; the locking and separation actions of the double-jointed block (3) are directly related to the relative movement direction of the locking object and are not limited by its own speed conditions; the double-jointed block (3) can use a line contact method to perform friction transmission with the locking object, and can also cooperate with a surface contact locking element or a rigid meshing element to greatly improve the load-bearing capacity; in addition, the functions of positive locking and reverse separation, positive separation and reverse locking, and bidirectional locking are realized through an inclination adjustment mechanism.

[0004] The present invention has a middle ring (28) which can rotate coaxially with the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) in the radial direction; the locking element includes a double-joint block (3) which is rotationally connected to the middle ring (28) and is also rotationally connected to the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) on one side of the middle ring (28), the two connection points being at different radial positions, so that when an angular displacement occurs between the middle ring (28) and the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) linked thereto through the double-joint block (3), the double-joint block (3) can be driven to tilt in the circumferential direction; the radial dimension of the double-joint block (3) can change in a negative correlation with the change of the angle between its long axis and the radial direction, and when the angle is maximum, the double-joint block (3) can be non-contact or pressure-free contact with the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) on the other side of the middle ring (28).

[0005] The double coupling block (3) of the present invention is a friction locking element or a rigid meshing locking element, which is directly driven by the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10).

[0006] The locking element of the present invention comprises a rack, a gear ring, a friction ring, a friction block, an expansion ring or a flexible ring, which can be driven by the double block (3), the middle ring (28), the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) to perform contact friction, rigid engagement or separation with the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10).

[0007] The double-jointed block (3) of the present invention is connected to a power-assisting device, which can apply a moment of force to tilt the double-jointed block (3) in a locking direction in an overrunning state.

[0008] The double-jointed block (3) of the present invention is connected with an inclination adjustment mechanism for wear compensation adjustment, and its technical types include eccentric wheel, rocker arm, connecting rod, cable, worm, thread, electric power, pneumatic power, hydraulic power or magnetic power mechanism.

[0009] The double-jointed blocks (3) of the present invention are divided into two groups, a forward tilting group and a backward tilting group. The double-jointed blocks (3) in the same group have the same tilting direction, tilting degree and radial size. The tilting degree adjustment mechanism can be used to make the sliding angles of the two groups of double-jointed blocks (3) have multiple combinations - the forward tilting group is larger than the backward tilting group, the forward tilting group is smaller than the backward tilting group, and the forward tilting group and the backward tilting group are equal, thereby realizing the functions of forward locking and reverse separation, forward separation and reverse locking, and bidirectional locking of the overall device.

[0010] The present invention has an external control device that can control the tilt adjustment mechanism, and its technical types include pull ropes, push rods, pull rods, knobs, buttons or sliders.

[0011] The present invention has built-in sensors, communication modules or power supply devices, which can be used to monitor the status of internal components. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] Figure 1 This is a structural diagram of an embodiment in which a double coupling block is installed in an inner ring;

[0013] Figure 2 yes Figure 1 Left view of;

[0014] Figure 3 This is a structural diagram of an embodiment in which a double coupling block is installed on an outer ring;

[0015] Figure 4 This is a structural diagram of an embodiment in which other types of locking elements are driven by a double coupling block;

[0016] Figure 5 Structural diagram of an embodiment in which a locking element is driven by a double coupling block and other components;

[0017] Figure 6 This is the structural diagram of the eccentric wheel inclination adjustment mechanism. DETAILED DESCRIPTION

[0018] Reference Figure 1 and Figure 2 The present invention is provided with a middle ring 28, which can rotate coaxially with the outer ring 1, clutch seat, inner ring 9 or central shaft 10 in the radial direction; the locking element includes a double-jointed block 3, which is rotatably connected to the middle ring 28, and is also rotatably connected to the outer ring 1, clutch seat, inner ring 9 or central shaft 10 on one side of the middle ring 28. The two connection points are at different radial positions, so that when angular displacement occurs between the middle ring 28 and the outer ring 1, clutch seat, inner ring 9 or central shaft 10 linked to it through the double-jointed block 3, the double-jointed block 3 can be driven to tilt in the circumferential direction; the radial dimension of the double-jointed block 3 can change inversely with the change of the angle between its long axis and the radial direction. When the angle is maximum, the double-jointed block 3 and the outer ring 1, clutch seat, inner ring 9 or central shaft 10 on the other side of the middle ring 28 may not be in contact or in pressure-free contact. Figure 1 and Figure 2The illustrated embodiment features an outer ring 1 and an inner ring 9, with a double link 3 mounted on the inner ring 9. One end of the double link 3, acting as a locking element, is rotatably connected to a cylindrical pin on the middle ring 28 via an oblong hole 2. Both ends can slide relative to each other along the oblong hole 2. Simultaneously, the double link 3 is rotatably connected to the inner ring 9 via a pin 4. These two connection points are located at different radial positions, allowing the double link 3 to rotate circumferentially with angular displacement between the middle ring 28 and the inner ring 9, and in turn limiting their angular displacement range. The middle ring 28 utilizes sliding, magnetically suspended, or roller-type rotational engagement with the outer ring 1 and inner ring 9 on the radially outer and inner sides, respectively. The double link block 3 tilts clockwise, and its radial dimension can change inversely with the angle between its long axis and the radial direction. When the outer ring 1 rotates clockwise relative to the inner ring 9, the double link block 3 also rolls in the same direction, causing the double link block 3 to tilt clockwise and reduce its radial dimension. When the double link block 3 reaches the limit position, the double link block 3 and the outer ring 1 may not contact or be in pressure-free contact, and the clutch is in an overrunning state. When the outer ring 1 rotates counterclockwise relative to the inner ring, the double link block 3 tilts counterclockwise and its radial dimension gradually increases until the two end points lock the outer ring 1 and the inner ring 9, or the outer ring 1 and the inner ring 9 are locked through one end point and the pin 4. The double link block 3 can be one or more than two distributed circumferentially, tilting in the same direction to achieve one-way locking or separation, or divided into two groups tilting in opposite directions to achieve two-way locking. The double block 3 can be a friction-type locking element, or it can have a rigid meshing locking structure at the end to mesh with the locking object; the locking element can be only the double block 3, or there can be other types of locking elements to cooperate with the double block 3, including but not limited to racks, gear rings, friction rings, friction blocks, expansion rings or flexible rings; the double block 3 can be a direct locking element, or it can be used as an indirect locking element to drive other types of locking elements. Figure 1 The structural scheme can also be as follows Figure 3 In reverse, the double-jointed block 3 is rotationally connected to the outer ring 1 through the pin 4, and is rotationally and slidingly connected to the double-jointed block 3 through the oblong hole 2. The middle ring 28 adopts sliding rotation cooperation, magnetic suspension rotation cooperation, or rotation cooperation with rollers on the radial outside and inside respectively with the outer ring 1 and the inner ring 9.

[0019] Figure 1 The double coupling block 3 of the embodiment is a friction-type locking element, which locks the outer ring 1 and the inner ring 9 through the two end points of the long shaft, or locks the outer ring 1 and the inner ring 9 through one end point and the pin shaft 4. A tooth profile can also be provided on the end point. At the same time, a rack that can engage with it for transmission is also provided on the outer ring 1, the clutch seat, the inner ring 9 or the middle shaft 10.

[0020] Reference Figure 4In the embodiment, there are multiple friction blocks 14, both ends of which are rotatably connected to the adjacent double-joint blocks 3. When the relative speed of the outer ring 1 and the inner ring 9 changes, the radial size of the double-joint blocks 3 also changes, thereby driving the friction blocks 14 to move closer to or away from the outer ring 1, thereby achieving the locking or separation of the clutch. Figure 5 In the illustrated embodiment, a flexible ring 15 wraps around the outer periphery of the central shaft 10, its ends pivotally connected to the ends of the dual coupling block 3. Changes in the radial dimensions of the dual coupling block 3 cause the flexible ring 15 to tighten or loosen the central shaft 10, thereby locking or disengaging the clutch. Locking elements include, but are not limited to, racks, gear rings, friction rings, friction blocks, expansion rings, or flexible rings. These elements are connected to the relatively movable dual coupling block 3, rollers 5, retainer 8, outer ring 1, clutch seat, inner ring 9, or central shaft 10, and can be driven by these elements to engage in contact friction, rigid meshing, or disengagement with the outer ring 1, clutch seat, inner ring 9, or central shaft 10.

[0021] Reference Figure 1 and 2 The resistance between the middle ring 28 and the outer ring 1 is greater than the resistance between the middle ring 28 and the inner ring 9. When the outer ring 1 and the inner ring 9 transition from the overrunning state to the engaged state, they can first cause the middle ring 28 and the inner ring 9 to undergo angular displacement. Alternatively, an elastic material may be provided between the distal end of the oblong hole 2 and the pin 11 as a booster. This preload forces the double coupling block 3 in the overrunning state toward the locking direction, but the preload is less than the force required to maintain the overrunning state. This prevents the locking function of the double coupling block 3 from malfunctioning without affecting the disengagement function. The booster may also be a magnetic device or other technical type.

[0022] Reference Figure 1 and Figure 6 . Figure 6 The illustrated embodiment shows an eccentric-type tilt adjustment mechanism. An eccentric 25, slidably connected to the double link 3, is fixed to the pin 11. Changing its eccentric orientation can alter the maximum sliding travel of the double link 3 and the pin 11, as well as the radial position of the eccentric 25's point of action on the inner wall of the oblong hole 2. Changing the eccentric orientation of the eccentric 25 also allows the tilt of the double link 3 to have varying sensitivities to the circumferential displacement of the pin 11. This can be used to adjust the tilt angle (i.e., the slip angle) of the double link 3 between the locked and overrunning states, thereby compensating for wear on transmission components or adjusting other functional requirements. The technology used for tilt adjustment mechanisms is not limited to eccentric mechanisms and may also include, but is not limited to, rocker arms, connecting rods, cables, worm gears, threads, electric, pneumatic, hydraulic, or magnetic mechanisms.

[0023] Reference Figure 1 and Figure 6, divide the double-linked blocks 3 into two groups, forward and backward, and the double-linked blocks 3 in the same group have the same inclination direction, inclination and radial size; through the action of the inclination adjustment mechanism, the two groups of double-linked blocks 3 have different sliding angle combinations - the forward group is larger than the backward group, the forward group is smaller than the backward group, and the forward group and the backward group are equal; when the sliding angles of the two groups of double-linked blocks 3 are not equal, the locking function of one group fails, and when the sliding angles of the two groups of double-linked blocks 3 are equal, their locking functions are normal, thereby realizing the functions of forward locking and reverse separation, forward separation and reverse locking, and two-way locking of the overall device.

[0024] Reference Figure 6 The pull rope 24 is connected to the pin 11. Pulling the pull rope from the outside can make the pin 11 move forward or reverse to control the inclination adjustment mechanism. The external control device can also be but not limited to a push rod, a pull rod, a knob, a button or a slider.

[0025] Position, speed, acceleration, temperature, pressure or torque sensors, communication modules or power supply devices are installed inside the device to monitor the status of internal components.

Claims

1. A double-block overrunning clutch comprising a locking element, directly connected to a clutch seat or a central shaft (10) or further comprising an outer ring (1) or an inner ring (9), connected to a clutch seat or a central shaft (10) via an outer ring (1) or an inner ring (9), characterized in that The invention relates to a locking element comprising a middle ring (28) which can rotate coaxially with the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) in the radial direction; a locking element comprising a double-jointed block (3) which is rotationally connected to the middle ring (28) and is also rotationally connected to the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) on one side of the middle ring (28); the two connection points are at different radial positions, so that when an angular displacement occurs between the middle ring (28) and the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) linked thereto through the double-jointed block (3), the double-jointed block (3) can be driven to tilt in the circumferential direction; the radial dimension of the double-jointed block (3) can change in a negative correlation with the change of the angle between its long axis and the radial direction; when the angle is maximum, the double-jointed block (3) does not contact or has no pressure contact with the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10) on the other side of the middle ring (28); The double coupling block (3) is a friction locking element or a rigid meshing locking element, which is directly driven by the outer ring (1), the clutch seat, the inner ring (9) or the middle shaft (10). An elastic material is connected to the double-jointed block (3) as a power-assisting device, which can apply a moment of force to the double-jointed block (3) to tilt in the locking direction in the overrunning state. The double block (3) is connected with an inclination adjustment mechanism capable of performing wear compensation adjustment. The inclination adjustment mechanism is an eccentric wheel. The double-jointed blocks (3) are divided into two groups, namely, a forward tilting group and a backward tilting group. The double-jointed blocks (3) in the same group have the same tilting direction, tilting degree and radial size. The tilting degree adjustment mechanism can be used to make the sliding angles of the two groups of double-jointed blocks (3) have multiple combinations: the forward tilting group is larger than the backward tilting group, the forward tilting group is smaller than the backward tilting group, and the forward tilting group and the backward tilting group are equal, thereby realizing the functions of forward locking and reverse separation, forward separation and reverse locking, and bidirectional locking of the overall device. An external control device can control the tilting degree adjustment mechanism, and the external control device is a pull rope.

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