A slow-release centrifugal declutching type of inclined strut clutch using a non-equal pre-tightening torque torsion spring

Abstract

The application provides a slow-release centrifugal disengagement type inclined support clutch using a non-equal pre-tightening torque torsion spring and relates to the field of aviation transmission system design. The clutch comprises a coaxially assembled outer ring and an inner ring; a freewheel is arranged between the inner ring and the outer ring and comprises a plurality of wedge blocks which are arranged in a ring shape between the inner ring and the outer ring, the rotation axis of the wedge blocks is parallel to the rotation axis of the inner ring, the outer contour of the wedge blocks comprises an upper cam and a lower cam which are in contact with the outer ring and the inner ring respectively, the connecting line of the contact points of the upper cam and the lower cam and the inner ring and the outer ring divides the wedge blocks into an engagement side and an overrun side, and the center of mass of the wedge blocks is located on the overrun side. The wedge blocks are subjected to different driving wedge block rotation torques, the original clutch function is optimized by arranging and adjusting the size of the torsion spring, the engagement impact problem of the centrifugal disengagement type clutch under high-speed operation conditions is solved, and the use safety of the clutch is improved.

Description

Technical Field

[0001] This invention relates to the field of aircraft transmission system design, and in particular to a slow-release centrifugal disengagement type oblique brace clutch that uses a non-uniform preload torque torsion spring. Background Technology

[0002] An overrunning clutch is a basic mechanical component that transmits torque in one direction. It can automatically switch transmission states by changing the speed and direction between the driving and driven components, and is often used to coordinate the operation of different power and transmission systems in mechanical systems. Among them, the wedge-type clutch features a wedge block that maintains the same wedge angle at different contact positions, exhibits self-locking characteristics during wedging, has sensitive disengagement performance under reverse conditions, and has a high load-bearing capacity, making it the most widely used in current industrial applications. Ordinary wedge-type clutches are usually designed for centrifugal disengagement to ensure service life and reduce wear between the wedge block and the inner ring raceway in the overrunning state. However, at excessively high clutch speeds, centrifugal torque can cause the wedge block to disengage from the inner ring raceway or even overturn. This prevents timely establishment of wedging conditions during clutch operation state switching, resulting in a delayed engagement time and generating a large instantaneous impact torque. This can easily damage weak components in the mechanical system, shorten service life, and even jeopardize operational safety. Summary of the Invention

[0003] This invention provides a slow-release centrifugal disengagement type inclined support clutch using a non-uniform preload torque torsion spring, the purpose of which is to solve the problem of excessive dynamic engagement impact of existing centrifugal disengagement inclined support clutches during high-speed operation.

[0004] To achieve the above objectives, embodiments of the present invention provide a slow-release centrifugal disengagement type inclined strut clutch employing a non-uniform preload torque torsion spring, comprising:

[0005] Coaxially assembled inner and outer rings;

[0006] A freewheel, disposed between an inner ring and an outer ring, includes a wedge. Several wedges are arranged in a ring between the inner and outer rings. The rotation axis of the wedge is parallel to the rotation axis of the inner ring. The outer contour of the wedge includes an upper cam and a lower cam that respectively contact the outer ring and the inner ring. The line connecting the contact points of the upper and lower cams with the inner and outer rings divides the wedge into an engagement side and an overrunning side. The center of mass of the wedge is located on the overrunning side.

[0007] The wedges are subjected to different torques that drive the wedges to rotate, and the magnitude of the torque on any one wedge is different from that on its adjacent wedges.

[0008] Preferably, the wedge has a first non-working surface and a second non-working surface, the first and second non-working surfaces are parallel to the rotation axis of the wedge, and the first and second non-working surfaces smoothly transition to form the upper cam. The wedge also has a third non-working surface, the third non-working surface and the second non-working surface are located on the same side of the rotation axis of the wedge, and the third non-working surface is connected to the second non-working surface. The third non-working surface and the first non-working surface smoothly transition to form the lower cam, and the included angle between the second and third non-working surfaces is 130-165 degrees.

[0009] Preferably, the free wheel further includes two fixed retaining rings, which are disposed between the inner ring and the outer ring and are coaxial with the inner ring. The two ends of the wedge are provided with second-order short shafts, and the fixed retaining rings are provided with through holes that are clearance-fitted with the smaller end of the second-order short shafts.

[0010] Preferably, a stop pin is provided between adjacent wedges, and a double torsion spring is provided on each wedge. The working sections of the double torsion spring are respectively sleeved on the second-order short shafts at both ends of the same wedge. The conjugate section of the double torsion spring abuts against the third non-working surface, and the support leg of the double torsion spring abuts against the stop pin.

[0011] Preferably, the outer ring has a connection hole for connecting to an external load element, and the inner ring has a transmission keyway for connecting to an external power element.

[0012] Preferably, the included angle between the second non-working surface and the third non-working surface is 150°.

[0013] Preferably, the fixed retaining ring is further provided with threaded holes, the threaded holes and the through holes are arranged alternately, and the threads at both ends of the retaining pin are in opposite directions.

[0014] The above-described solution of the present invention has the following beneficial effects:

[0015] This application, based on the engagement and overrunning functions of a conventional inclined strut clutch, optimizes the original clutch function by adjusting the arrangement of the torsion springs and the magnitude of the torque. It solves the engagement impact problem of centrifugal disengagement clutches under high-speed operating conditions, improves the safety of clutch use, and maximizes the advantages of centrifugal disengagement clutches by utilizing the centrifugal disengagement effect to make the wedge block and inner ring separate from each other during overrunning, achieving contactless overrunning, significantly reducing friction and wear, and extending the service life of the clutch.

[0016] Other features and advantages of the present invention will be described in detail in the following detailed description section. Attached Figure Description

[0017] Figure 1 This is a cross-sectional schematic diagram of the present invention;

[0018] Figure 2 This is a half-sectional schematic diagram of the present invention;

[0019] Figure 3 This is a schematic diagram showing the contact between the wedge and the outer and inner rings;

[0020] Figure 4 This is a schematic diagram of a double torsion spring;

[0021] Figure 5 This is a first-person view of the wedge.

[0022] Figure 6 This is a second-view diagram of the wedge.

[0023] Figure 7a This is the first stage state diagram of the wedge block;

[0024] Figure 7b This is the second-stage state diagram of the wedge block;

[0025] Figure 7c This is the third stage state diagram of the wedge block;

[0026] Figure 7d This is the state diagram of the fourth stage of the wedge block.

[0027] [Explanation of Labels in the Attached Image]

[0028] 1-Outer ring, 2-Inner ring, 3-Wedge block, 31-Upper cam, 32-Lower cam, 33-Center of mass, 34-First non-working surface, 35-Second non-working surface, 36-Third non-working surface, 37-Second-order short shaft, 4-Fixed retaining ring, 41-Through hole, 42-Threaded hole, 5-Stop pin, 6-Double torsion spring, 61-Working section, 62-Conjugate section, 63-Support leg, 7-Connecting hole, 8-Transmission keyway. Detailed Implementation

[0029] To make the technical problems, technical solutions and advantages of the present invention clearer, a detailed description will be given below in conjunction with the accompanying drawings and specific embodiments.

[0030] like Figure 1-3As shown, an embodiment of the present invention provides a slow-release centrifugal disengagement type inclined bearing clutch using a non-uniform preload torque torsion spring, comprising an outer ring 1, an inner ring 2, and a free wheel. The inner ring 2 and outer ring 1 are coaxially assembled, and the free wheel is disposed between the inner ring 2 and outer ring 1. The free wheel includes multiple wedges 3 arranged in a ring between the inner ring 2 and outer ring 1. The virtual circle containing the wedges 3 is concentric with both the inner ring 2 and outer ring 1. The rotation axis of the wedges 3 is parallel to the rotation axis of the inner ring 2. The outer contour of the wedges 3 includes an upper cam 31 and a lower cam 32. The upper cam 31 contacts the outer ring 1, and the lower cam 32 contacts the inner ring 2. The contact point between the upper cam 31 and the outer ring 1 is point A, and the contact point between the lower cam 32 and the inner ring 2 is point B. The line connecting points A and B divides the wedge 3 into an engagement side and an overrunning side. The center of mass 33 of the wedge is located on the overrunning side, thus creating the disengagement condition for the clutch.

[0031] The wedge 3 rotates under the action of different torques, and the magnitude of the torque on any wedge 3 is different from that on the adjacent wedge 3.

[0032] In this embodiment, wedges 3, subjected to different torques, are arranged diagonally between the inner ring 2 and the outer ring 1 in a unified direction, which can meet the power transmission requirements from the inner ring 2 to the outer ring 1. When the rotational speed of the inner ring 2 exceeds that of the outer ring 1, the wedges 3 abut and wed with the outer circumferential raceway of the inner ring 2 and the inner circumferential raceway of the outer ring 1, and the power is transmitted to the outer ring 1 through the inner ring 2, driving the outer ring 1 to rotate; when the rotational speed of the outer ring 1 exceeds that of the inner ring 2, the wedges 3 do not transmit power.

[0033] Under high-speed conditions, the wedge 3 subjected to low torque will temporarily disengage due to centrifugal force, while the wedge 3 subjected to high torque will not disengage. When the clutch transitions from a high-speed overrunning state to a high-speed engaging state, the wedge 3 subjected to high torque quickly meets the clutch wedging condition, while the wedge 3 subjected to low torque, due to excessive centrifugal force, is temporarily "lifted" from the raceway surface of the inner ring 22 and does not meet the wedging condition, causing the outer ring 1 speed to decrease further. The decrease in the speed of the outer ring 1 reduces the centrifugal torque of the wedge 3 subjected to low torque, and the wedge 3 subjected to low torque gradually "falls back." As the lower cam 32 of the wedge 3 subjected to low torque resumes contact with the inner ring 2, the wedge 3 subjected to low torque also quickly meets the wedging condition, and the clutch completes the dynamic engagement process from the overrunning state to the engaging state.

[0034] In some embodiments of this application, such as Figure 5 , 6The wedge block 3 is provided with a first non-working surface 34 and a second non-working surface 35. The first non-working surface 34 and the second non-working surface 35 are parallel to the rotation axis of the wedge block 3. The upper end of the first non-working surface 34 and the upper end of the second non-working surface 35 smoothly transition to form the aforementioned upper cam 31. The wedge block 3 is also provided with a third non-working surface 36. The third non-working surface 36 and the second non-working surface 35 are located on the same side of the rotation axis of the wedge block 3. The upper end of the third non-working surface 36 is connected to the lower end of the second non-working surface 35. The lower end of the third non-working surface 36 smoothly transitions to the lower end of the first non-working surface 34 to form a lower cam 32. The included angle D between the second non-working surface 35 and the third non-working surface 36 is 130-165 degrees.

[0035] Preferably, the angle D between the second non-working surface 35 and the third non-working surface 36 is 150°.

[0036] Furthermore, in combination Figure 1 and 2 The free wheel also includes two fixed retaining rings 4, which are annular in shape and positioned between the inner ring 2 and the outer ring 1, covering the space formed by the inner ring 2 and the outer ring 1. The wedge block 3 is surrounded by the two fixed retaining rings 4, the inner ring 2, and the outer ring 1. The center of the fixed retaining ring 4 coincides with the center of the inner ring 2, and the fixed retaining ring 4 is provided with through holes 41 arranged in a circular array. The two ends of the wedge block 3 are provided with second-order short shafts 37, which are boss-shaped and include a smaller end and a larger end. In this embodiment, the smaller end is connected to the two ends of the wedge block 3 through the larger end, and the smaller end is clearance-fitted with the aforementioned through holes 41, so that when the wedge block 3 rotates around the second-order short shaft 37 between the inner ring 2 and the outer ring 1, it can move slightly in the radial direction of the through holes 41, avoiding over-constraint when the wedge block 3 rotates.

[0037] Furthermore, a stop pin 5 is provided between adjacent wedge blocks 3, and a stop pin 5 is provided on the wedge block 3 as shown in the figure. Figure 4 The double torsion spring 6 shown has its working section 61 fitted onto the second-order short shafts 37 at both ends of the same wedge block 3, specifically fitted onto the larger end. The conjugate section 62 of the double torsion spring 6 abuts against the third non-working surface 36, and the support leg 63 of the double torsion spring 6 abuts against the stop pin 5.

[0038] Preferably, the third non-working surface 36 is a smooth plane to reduce the frictional resistance of the conjugate segment 62 on the third non-working surface 36.

[0039] In this embodiment, the double torsion spring 6 is divided into a high-torque torsion spring and a low-torque torsion spring. The torque of the double torsion spring 6 can be changed by the arm angle, leg length, spring wire diameter, spring mean diameter, and number of working coils of the torsion spring in its natural state. The wedge block 3 with the high-torque spring and the wedge block 3 with the low-torque spring are arranged alternately in a ring.

[0040] In some other embodiments, the double torsion spring 6 is divided into a large torque torsion spring, a small torque torsion spring, and a medium torque torsion spring. Each double torsion spring 6 is mounted on the wedge block 3. The large torque torsion spring, the medium torque torsion spring, and the small torque torsion spring are arranged to form a torsion spring group. The double torsion springs 6 in each torsion spring group are arranged in the same order. The torsion spring groups with wedge blocks 3 are circumferentially symmetrically distributed to ensure that the wedge blocks 3 with the same torque engage at the same time and avoid the occurrence of unbalanced forces.

[0041] Similarly, medium torque torsion springs can be further divided into medium-high torque torsion springs, medium-medium torque torsion springs, and medium-low torque torsion springs.

[0042] Setting up multiple different torque distribution methods can further reduce the impact on the clutch shaft end and protect the clutch's peripheral components while meeting the requirements of dynamic clutch engagement.

[0043] A threaded hole 42 is also provided on the fixed retaining ring 4. The threaded hole 42 is arranged alternately with the aforementioned through hole 41. The threaded hole 42 is used to screw the aforementioned retaining pin 5. The two ends of the retaining pin 5 are provided with threads in opposite directions to fix it and limit the rotation angle of the wedge block 3, so as to ensure that the wedge block 3 does not flip over when it is centrifugally disengaged.

[0044] Furthermore, the outer ring 1 has a connecting hole 7 for connecting to external components, and the inner ring 2 has a transmission keyway 8 for connecting to external power components. Generally, the inner ring 2 serves as the power input and the outer ring 1 serves as the power output. In actual working conditions, it is also possible to transmit power from the outer ring 1 to the inner ring 2.

[0045] The dynamic bonding process in this application is divided into the following steps: Figures 7a-7d The diagram shows four stages, with the left side featuring a wedge with a small torsion spring and the right side featuring a wedge with a large torsion spring. The first stage is the overtaking stage, the second stage is the wedge engagement stage with the wedge with the large torsion spring, the third stage is the incomplete wedge engagement stage, and the fourth stage is the completed wedge engagement stage.

[0046] In the first stage, the outer ring 1 is connected to power and a load, while the inner ring 2 rotates at 0 or less than the outer ring 1 (i.e., n). 外 >n 内 The speed of wedge 3 around the clutch center changes with the speed of outer ring 1. During this stage, the upper cam 31 of the wedge 3 with the large torque torsion spring abuts against the outer ring 1, and the lower cam 32 abuts against the inner ring 2; the upper cam 31 of the wedge 3 with the small torque torsion spring abuts against the outer ring 1, and the lower cam 32 separates from the inner ring 2.

[0047] In the second stage, the inner ring 2 is powered, and its speed gradually increases, while the outer ring 1 is depowered, and its speed gradually decreases under the load torque. When the speed of the inner ring 2 equals the speed of the outer ring 1 (i.e., n...), the speed of the outer ring 1 gradually decreases. 外 =n内 The outer ring 1 has a decreasing speed tendency, while the inner ring 2 has an increasing speed tendency. At this point, the second stage of dynamic engagement of the clutch begins. The inner ring 2 speed increases, and the outer ring 1 speed decreases, satisfying n_outer < n_inner. The wedge block 3 with the large torque torsion spring satisfies the wedge engagement condition, completing the wedge engagement of the large torque torsion spring.

[0048] In the third stage, the outer ring 1 is unpowered, and its speed continues to decrease under the load torque. The inner ring 2 is powered and its speed gradually increases. Based on the second stage, the wedge 3 with a large torque torsion spring has completed its wedging action and can transmit some torque, reducing the downward trend of the outer ring 1's speed. However, this torque is insufficient to drive the load torque loaded on the outer ring 1. At this time, the clutch with a small torque torsion spring follows the decrease in the speed of the outer ring 1, the centrifugal effect of the clutch weakens, and the degree to which each wedge 3 with a small torque torsion spring "lifts" gradually decreases.

[0049] In the fourth stage, the outer ring 1 is unpowered and its speed continues to decrease under the load torque. The inner ring 2 gradually increases its speed under the drive of rotational power. As the speed of the inner ring 2 further increases in the third stage, the speed of the outer ring 1 further decreases. The wedge block 3 with the small torque torsion spring falls back, and the upper cam 31 of the wedge block 3 with the small torque torsion spring engages with the outer ring 1, while the lower cam 32 re-engages with the inner ring 2. At this time, the speed of the inner ring 2 is higher than that of the outer ring 1, and the wedge block 3 with the small torque torsion spring instantly meets the wedge engagement condition. All wedge blocks 3 begin to transmit torque, and the speeds of the inner ring 2 and outer ring 1 of the clutch become consistent, satisfying n. 外 =n 内 The wedging action is completed, and the entire dynamic engagement process of the clutch ends.

[0050] The above description represents the preferred embodiments of the present invention. It should be noted that those skilled in the art can make various improvements and modifications without departing from the principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A slow-release centrifugal disengagement type diagonal brace clutch using a non-uniform preload torque torsion spring, characterized in that, include: Coaxially assembled outer and inner rings; A freewheel, disposed between an inner ring and an outer ring, includes a wedge. Several wedges are arranged in a ring between the inner and outer rings. The rotation axis of the wedge is parallel to the rotation axis of the inner ring. The outer contour of the wedge includes an upper cam and a lower cam that respectively contact the outer ring and the inner ring. The line connecting the contact points of the upper and lower cams with the inner and outer rings divides the wedge into an engagement side and an overrunning side. The center of mass of the wedge is located on the overrunning side. The wedge is subjected to different torques that drive its rotation; The wedge has a first non-working surface and a second non-working surface, which are parallel to the rotation axis of the wedge. The first and second non-working surfaces smoothly transition to form the upper cam. The wedge also has a third non-working surface, which is located on the same side of the rotation axis of the wedge as the second non-working surface and is connected to the second non-working surface. The third non-working surface smoothly transitions to the first non-working surface to form the lower cam. The included angle between the second and third non-working surfaces is 130-165 degrees. The free wheel also includes two fixed retaining rings, which are disposed between the inner ring and the outer ring and are coaxial with the inner ring. The two ends of the wedge are provided with second-order short shafts, and the fixed retaining rings are provided with through holes that are clearance-fitted with the smaller end of the second-order short shafts. A stop pin is provided between adjacent wedges, and a double torsion spring is provided on the wedge. The working sections of the double torsion spring are respectively sleeved on the second-order short shafts at both ends of the same wedge. The conjugate section of the double torsion spring abuts against the third non-working surface, and the support leg of the double torsion spring abuts against the stop pin. The double torsion springs are torsion springs with different torques; In the first stage, the outer ring is connected to power and a load, while the inner ring's rotational speed n 内 =0 or less than the outer ring speed n 外 The speed of the wedge block around the clutch center changes with the speed of the outer ring. During this stage, the upper cam of the wedge block with the large torque torsion spring abuts against the outer ring, and the lower cam abuts against the inner ring; the upper cam of the wedge block with the small torque torsion spring abuts against the outer ring, and the lower cam separates from the inner ring. In the second stage, power is applied to the inner ring, and its speed gradually increases. Power is removed from the outer ring, and its speed gradually decreases under the load torque. When the inner ring's speed n... 内 Equal to the outer ring speed n 外 At this time, the outer ring tends to decrease in speed, while the inner ring tends to increase in speed. This marks the beginning of the second stage of dynamic clutch engagement, where the inner ring speed increases and the outer ring speed decreases. 外 Decrease, satisfying n 外 <n 内 The wedge with a large torque torsion spring satisfies the wedge engagement condition and engages, thus completing the wedge engagement of the large torque torsion spring. In the third stage, the outer ring is unpowered and its speed continues to decrease under the load torque. The inner ring, powered, gradually increases its speed. Based on the second stage, the wedges with large torque torsion springs have completed their wedging action and can transmit some torque, reducing the decreasing trend of the outer ring's speed. However, this torque is insufficient to drive the load torque applied to the outer ring. At this time, the clutches with small torque torsion springs follow the decrease in the outer ring's speed, the centrifugal effect of the clutch weakens, and the degree to which each wedge with a small torque torsion spring "lifts" gradually decreases. In the fourth stage, the outer ring is unpowered and its speed continues to decrease under the load torque. The inner ring, driven by rotational power, gradually increases its speed. As the inner ring speed further increases in the third stage, the outer ring speed further decreases. The wedge with the small torque torsion spring falls back down, and the upper cam of the wedge with the small torque torsion spring engages with the outer ring, while the lower cam re-engages with the inner ring. At this point, the inner ring speed is n. 内 Higher than the outer ring speed n 外 The wedges with small torque torsion springs instantly meet the wedging conditions, all wedges begin to transmit torque, and the inner and outer rings of the clutch rotate at the same speed, satisfying n. 外 =n 内 The wedging action is completed, and the entire dynamic engagement process of the clutch ends.

2. The slow-release centrifugal disengagement type inclined strut clutch using a non-uniform preload torque torsion spring according to claim 1, characterized in that: The outer ring has a connection hole for connecting to an external load element, and the inner ring has a transmission keyway for connecting to an external power element.

3. The slow-release centrifugal disengagement type diagonal brace clutch using a non-uniform preload torque torsion spring according to claim 2, characterized in that: The angle between the second non-working surface and the third non-working surface is 150°.

4. The slow-release centrifugal disengagement type diagonal brace clutch using a non-uniform preload torque torsion spring according to claim 1, characterized in that: The fixed retaining ring is also provided with threaded holes, which are arranged alternately with the through holes, and the threads at both ends of the retaining pin are in opposite directions.

Images