A high-speed overrunning clutch

Abstract

The present invention provides a high-speed overrunning clutch including a housing and a clutch, wherein the housing portion is mainly composed of a housing body, a bearing, a threaded sealing cover, a housing end cover, a pressure cover, etc., and the clutch portion is composed of an output shaft, an outer ring, an input shaft, a wedge, a spring, a baffle, a hydraulic pump, an outer ring end cover, an oil slinger, a bearing, a fastener, a sealing member, etc., and the middle of the housing is a cavity structure, and the cavity structure accommodates the housing of the clutch rotary structure; the present invention can realize high-speed overrunning and high-speed wedging, and prevent the active end from being dragged and rotated, and has a box-type high-speed overrunning clutch with a built-in hydraulic pump, providing a high-speed overrunning clutch with perfect performance of forced lubrication, anti-drag rotation, non-contact sealing, and self-cooling.

Description

Technical Field

[0001] The invention relates to a mechanical transmission device, in particular to a high-speed overrunning clutch with a built-in hydraulic pump and the function of preventing the driving end from being dragged and rotating, and belongs to the category of basic mechanical transmission parts. Background Art

[0002] The existing overrunning clutch is generally composed of an outer ring, an inner ring wedging component, etc. When overrunning (i.e., the inner and outer rings move relative to each other), the internal wedging component rubs against the inner and outer rings, and an idling torque is formed due to friction and grease damping. When the passive end overruns at high speed, it will drive the active end to rotate together. The greater the speed difference, the greater the idling torque, which will drive the active end drive device (such as a motor) to rotate together, which will have an adverse effect on the motor and cause wear of the active end seal.

[0003] This problem is particularly evident in high-speed clutches, such as in patent application number: CN201510016506.6 "A non-contact overrunning clutch", which uses a hydraulic pump for forced lubrication. During overrunning, the oil flows through the pump nozzle of the hydraulic pump, enters the hydraulic pump and is ejected from the pump outlet, achieving the purpose of forced lubrication. However, the increase in the kinetic energy of the oil to the pump will drive the pump to rotate together with the active end, thus reducing the oil entering the pump, and thus failing to achieve the effect of forced lubrication. In order to avoid this problem, it is necessary to add components such as electromagnetic brakes at the active end, which makes the structure complex and increases the cost.

[0004] In addition to the aforementioned disadvantages, in the patent application number: CN201510016506.6 "A non-contact overrunning clutch", since both the active and passive ends are sealed with oil seals, the internal oil is in a completely closed state. When rotating at high speed, the oil seals heat up seriously and are easily damaged. In addition, as the oil temperature inside the clutch increases, the internal pressure also increases, and there is a risk of high-temperature oil bursting the oil seal and spraying out. Summary of the invention

[0005] The purpose of the present invention is to provide a box-type high-speed overrunning clutch with a built-in hydraulic pump that can achieve high-speed overrunning and high-speed wedging and prevent the active end from being dragged and rotated, thereby overcoming the defects of the prior art mentioned in the background technology and providing a high-speed overrunning clutch with perfect performance such as forced lubrication, anti-drag rotation, non-contact sealing and self-cooling.

[0006] In order to achieve the above-mentioned purpose, the technical solution adopted by the present invention is as follows: a high-speed overrunning clutch, comprising a housing and a clutch, wherein the housing is provided with bearings at both ends and a cavity structure in the middle, and the cavity structure accommodates a housing of a clutch rotating structure, wherein the housing comprises a housing body, a fan is provided on one side of the housing body, and a housing end cover is provided on the other side, a protective cover is provided outside the fan and the housing end cover, and a sealing cover and a centrifugal brake assembly consisting of a plurality of centrifugal blocks, an annular tension spring, and a brake disc are also provided outside the housing end cover;

[0007] The clutch comprises an output shaft, an input shaft, an outer ring, and an outer ring end cover;

[0008] One end of the output shaft extends into the box body from the box end cover side, and the shaft end extends out of the box body from the inner hole of the bearing and is supported by the bearing; a threaded sealing cover is provided on the outer side of the bearing, and an inner hole on the threaded sealing cover is provided with an internal thread and a vent hole, the threaded sealing cover is in clearance with the output shaft, and the vent hole is provided at the upper part of the inner hole of the threaded sealing cover;

[0009] A plurality of wedges are arranged in the annular cavity formed between the outer ring and the input shaft, and a support spring is passed through the middle of the wedge, and the support spring makes the wedge and the inner wall of the outer ring tight and rotate with the outer ring; the height of the wedge is greater than the distance of the radial gap between the outer ring and the input shaft; the wedge is in a diagonal support state;

[0010] The outer ring end surface is also provided with a baffle, an annular gap is provided between the baffle and the input shaft in the radial direction, and a hydraulic pump is provided on the input shaft close to the baffle;

[0011] The outer side of the outer ring end cover is also coaxially connected to an oil slinger ring, and the oil slinger ring is also evenly provided with a number of notches on its outer circle. The oil slinger ring is a hollow rotating body, and an annular cavity is formed between the oil slinger ring and the outer ring end cover. The outer ring end cover is provided with a number of axial small holes near the inner cavity of the oil slinger ring, and the small holes connect the cavity where the hydraulic pump is located and the cavity where the oil slinger ring is located.

[0012] A further improvement is that the brake disc is fastened to the input shaft extending out of the box body with a connecting piece, and a plurality of blocks are arranged inside the brake disc to divide the circumference of the inner cavity of the brake disc into a plurality of parts; a centrifugal block is arranged between adjacent blocks, and the block and the centrifugal block arranged between them form a circular ring structure, grooves are arranged on both sides of the circular ring structure, and an annular tension spring connected end to end is built into the groove, and the annular tension spring enables the centrifugal block to move toward the input shaft and hold the sealing cover fixed on the outside of the box end cover.

[0013] A further improvement is that one end of the outer ring is connected to the output shaft through a flange, and the other end is connected to the outer ring end cover; one end of the input shaft is inserted into the outer ring, and the other end passes through the outer ring end cover and is installed opposite to the output shaft and extends out of the box body.

[0014] A further improvement is that a guide plate and an oil filling cup are provided on the upper part of the box body and between the inner side of the box end cover and the oil slinger ring.

[0015] A further improvement is that the cross-sectional center of the wedge block is circular, adjacent wedge blocks are arranged with a slight gap between them, and each of them rotates around the central circle axis.

[0016] A further improvement is that the guide plate is a component composed of an upper plate, a baffle plate and a lower plate, and is fixed to the box end cover with screws; an oil filling cup is provided on the upper part of the box body corresponding to the upper plate, one side of the baffle plate is close to the inner side of the box end cover, and the other side is in clearance with the end face of the oil slinger ring, and the lower plate is inserted into the inner cavity of the oil slinger ring from the inner end face of the box end cover at an angle downward from the gap between the oil slinger ring and the input shaft.

[0017] A further improvement is that the hydraulic pump includes a pump body and a plurality of pump nozzles, the pump body is a hollow rotating body with small ends and a large middle, one end of the pump body is inserted into the annular gap between the baffle and the input shaft, the outer circle part of the pump body inserted into the baffle has a plurality of annular grooves, the outer diameter of the annular grooves matches the inner hole gap of the baffle, the hole at the other end of the pump body is mounted in cooperation with the input shaft, and is connected to the input shaft with fasteners.

[0018] A further improvement is that the pump body is evenly provided with 2 to 6 pump nozzles in the radial direction, one end of the pump nozzle is welded or threaded perpendicular to the pump body, and the other end is bent toward the input shaft, and the pump nozzle connects the inner cavity of the pump body with the outside.

[0019] A further improvement is that the input shaft is a multi-step stepped shaft, one end of which is centrally punched with a hole and connected to a radial hole on the input shaft, and the position of the radial hole is aligned with the oil slinger.

[0020] Compared with the prior art, the innovation of the present invention lies in: (1) Since the clutch is mainly used in high-speed working conditions, when the oil slinger ring rotates at high speed, the oil forms an annular oil layer on the inner wall of the oil slinger ring under the action of centrifugal force, and enters the cavity where the hydraulic pump nozzle is located along the small hole on the outer ring end cover, forming an annular oil layer on the inner wall of the outer ring and rotating at basically the same speed as the outer ring. As the oil layer thickens, the pump nozzle is immersed in the oil layer.

[0021] When the clutch is in the overrunning state, the pump nozzle inlet is in the opposite direction of the oil movement direction, so the oil enters the inner cavity of the pump body, accumulates to a certain pressure, and is ejected from the axial groove on the wedge side of the pump body, flows along the input shaft through the wedge joint, and forms an oil layer covering the input shaft surface. The wedge rotates with the outer ring, so the wedge passes through the oil layer at high speed and is lifted by the buoyancy of the oil, reaching a non-contact overrunning state with the input shaft surface, without wear and heat, and the clutch achieves high-speed overrunning.

[0022] When the input shaft gradually accelerates, the speed difference between the output shaft and the input shaft decreases, the relative speed between the oil layer and the pump nozzle decreases, the oil entering the pump body decreases, the oil lifting force on the wedge block gradually decreases, and the wedge block resumes contact with the input shaft under the action of the spring force. At the moment when the input shaft exceeds the output shaft speed, the clutch wedges and transmits torque, thereby achieving engagement at high speed.

[0023] (2) When the output shaft is overrunning at high speed, the relative movement between the wedge block and the input shaft and the relative movement between the oil layer and the pump nozzle will cause the input shaft to rotate. Another function of the invention is to adjust the braking force of the brake assembly, keep the input shaft stationary, and protect the drive motor and other equipment. When the input shaft has power input, the braking force can be almost ignored, the centrifugal block will move to the outer periphery of the brake disc, loosen the sealing cover, lose the clamping force, and operate without heat and wear.

[0024] (3) A threaded sealing cover is provided on the outside of the bearing to compress the bearing, and an internal thread is provided on its inner hole to match the shaft clearance. The rotation direction of the internal thread is designed to bring external air into the inside of the box body when the output shaft rotates, thereby playing a role of non-contact sealing. A vent hole is also provided on the diameter of the threaded sealing cover. When installed, the vent hole faces upward to prevent the internal oil from flowing out. The outlet of the vent hole is close to the high pressure area to enhance the effect of thread sealing.

[0025] The invention has small wear, low heat generation, no drag and long service life, and reliably realizes the functions of high-speed overtaking and high-speed wedging. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 : It is the front view of the high-speed overrunning clutch of the present invention;

[0027] Figure 2 :for Figure 1 AA section view;

[0028] Figure 3 :for Figure 1 BB cross-sectional view;

[0029] Figure 4 :for Figure 1 CC section view;

[0030] Figure 5 :for Figure 1 EE profile of

[0031] Figure 6 : It is the front view of the high-speed overrunning clutch hydraulic pump of the present invention;

[0032] Figure 7 :for Figure 6 FF cross-sectional view;

[0033] Figure 8: It is the front view of the threaded sealing cover of the high-speed overrunning clutch of the present invention;

[0034] Fig. 9 : It is the front view of the guide plate of the high-speed overrunning clutch of the present invention;

[0035] Fig.10 : It is the left view of the guide plate of the high-speed overrunning clutch of the present invention;

[0036] Figure numerals: 1—output shaft, 2—setting screw, 3—fan, 4—threaded sealing cover, 5—sealing ring a, 6—bearing a, 7—screw a, 8—box body, 9—screw b, 10—outer ring, 11—lifting ring, 12—screw c, 13—baffle, 14—hydraulic pump, 15—pin, 16—outer ring end cover, 17—bearing b, 18—oil throwing ring, 19—screw d, 20—screw e, 21—annular tension spring, 22—stopper, 23—screw f, 24—sealing cover, 25 —guide plate, 26—input shaft, 27—protective cover, 28—oil seal, 29—brake disc, 30—bearing c, 31—sealing ring b, 32—centrifugal block, 33—casing end cover, 34—screw g, 35—sealing ring c, 36—screw h, 37—sealing ring d, 38—sealing ring e, 39—oil, 40—drain plug, 41—wedge block, 42—support spring, 43—screw i, 44—bearing d, 45—screw j, 46—protective cover, 47—oil mark, 48—oil filling cup. DETAILED DESCRIPTION

[0037] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0038] like Figure 1-5 As shown, a high-speed overrunning clutch is composed of a housing part and a clutch part;

[0039] The box body is mainly composed of a box body 8, a bearing a, a threaded sealing cover 4, a fan 3, a protective cover 46, a box body end cover 33, a guide plate 25, a bearing c, a sealing cover 24, a brake disc 29, a stopper 22, a centrifugal block 32, an annular tension spring 21, a protective cover 26, a lifting ring 11, an oil mark 47, an oil filling cup 48, an oil drain plug 40 and fasteners, seals and the like; the box body is a box body with supporting bearings at both ends, an intermediate cavity that can accommodate the rotation of the clutch part, and necessary seals are arranged on the joint surface of the parts; oil 39 can be injected into the box body 8, the box body 8 is provided with a support, which can be fixed, and a fan 3 and a protective cover 46 are arranged on one side of the outside of the box body 8; a centrifugal brake assembly composed of a plurality of centrifugal blocks 32, an annular tension spring 21, a brake disc 29, a protective cover 26 and the like is also arranged on the outside of the box body 8, and an oil filling cup 48, an oil drain plug 40, a lifting ring 11, an oil mark 47 and other accessories are also arranged at appropriate positions on the periphery of the box body 8.

[0040] The clutch part is composed of output shaft 1, outer ring 10, input shaft 26, wedge block 41, support spring 42, baffle 13, hydraulic pump 14, outer ring end cover 16, oil slinger 18, bearing d, bearing b, fasteners, seals and the like.

[0041] The output shaft 1 is a rotating body with a flange at one end, which can be installed into the box body 8 from the box end cover 33 side, and the output shaft end extends out of the box body 8 from the inner hole of the bearing a and is supported by the bearing a. The fan 3 is fastened to the extended output shaft 1 and can rotate with the output shaft 1, and a protective cover 46 is fixed on the box body 8 for protection.

[0042] A threaded sealing cover 4 is provided on the outside of the bearing a (see Figure 8 ), the bearing a can be compressed, the inner hole of the threaded sealing cover 4 is provided with an internal thread 4-2 which is clearance-matched with the output shaft 1, and the rotation direction of the thread 4-2 is designed so that when the output shaft 1 rotates, external air is brought into the box body 8, thereby playing a role of non-contact sealing.

[0043] A vent hole 4-1 is also provided on the diameter of the threaded sealing cover 4. When installed, the vent hole is arranged at the upper part of the inner hole of the threaded sealing cover to prevent the internal oil 39 from flowing out. The vent hole is close to the high pressure area to enhance the sealing effect.

[0044] The flange end of the output shaft 1 is coaxial with the outer ring 10 in the box body 8 and connected by screws 9. A bearing d is provided near the center of the flange end. The outer ring 10 is a stepped cylindrical rotating part, one end of which is flange-connected to the output shaft 1 and the other end is connected to the outer ring end cover 16. The outer ring end cover 16 is coaxially positioned with the outer ring 10 and fastened with screws 36. A bearing b is provided inside the outer ring end cover 16.

[0045] The input shaft 26 is a multi-step stepped shaft, one end of which is centrally punched and connected to the radial hole on the shaft. One end of the input shaft 26 with a hole penetrates into the outer ring 10 and extends into the bearing d for positioning. The other end passes through the outer ring end cover 16 and is positioned with the bearing b and installed opposite to the output shaft 1. After the input shaft 26 is installed, it also extends out of the box body 8. During installation, the box body end cover 33 and the box body 8 are positioned through the stopper and fastened with screws 34. The box body end cover 33 is provided with a bearing c inside and a sealing cover 24 outside.

[0046] The brake disc 29 of the centrifugal brake assembly is fastened to the input shaft 26 extending out of the box body 8 with a connecting piece. The outer circle of the brake disc 29 is provided with a flange, and a plurality of blocks 22 are arranged inside it. The blocks 22 divide the inner circumference of the brake disc 29 into several parts. During installation, the blocks 22 and the brake disc 29 are connected with screws 20.

[0047] There are a plurality of stoppers 22 , and a centrifugal block 32 is disposed between each of the adjacent stoppers 22 , and a gap is left between the centrifugal block 32 and the stoppers 22 , so that the centrifugal block 32 can move in the radial direction.

[0048] A plurality of centrifugal blocks 31 and stoppers 22 form a circular ring, grooves are provided on both sides of the circular ring, and an annular tension spring 21 connected end to end is built in. The radial width of the groove of the stopper 22 is greater than the radial width of the groove of the centrifugal block 32, so that the force of the annular tension spring 21 is completely applied to the centrifugal block 32, and the centrifugal block 32 moves toward the center and is tightly fixed on the sealing cover 24 on the outside of the box end cover 33. At this time, the braking force, that is, the torque of the input shaft 26, can be adjusted by adjusting the length of the annular spring 21.

[0049] In the annular cavity between the outer ring 10 and the input shaft 26, a plurality of wedge blocks 41 are arranged on the circumference thereof. The center of the cross section of the wedge blocks 41 is circular, and the wedge blocks 41 are closely arranged with slight gaps between them. The wedge blocks 41 can rotate around the center circle respectively.

[0050] The front and rear end surfaces of the wedge block 41 are provided with 1 to 4 spring holes (the number depends on the length of the wedge block 41), and a support spring 42 is passed through the middle. The support spring 42 is connected end to end to tighten the wedge block 41 and the inner wall of the outer ring 10 and rotate with the outer ring 10.

[0051] A baffle 13 is provided on the stepped end face of the outer ring 10 outside the wedge block 41. Since the height of the wedge block 41 is greater than the distance of the radial gap between the outer ring 10 and the input shaft 26, the wedge block 41 is in a diagonal bracing state. For a single wedge block 41, only one side of the spring hole is pressed on the support spring 42. The wedge block 41 has a moment of contact with the outer ring 10 and the input shaft 26. This moment makes the wedge block 41 keep in contact with the outer ring 10 and the input shaft 26 surface, forming the principle of a diagonal bracing wedge block clutch, and realizing the basic functions of overrunning and wedging.

[0052] In order to achieve high-speed overrunning and high-speed wedging functions, an annular gap is left in the radial direction between the baffle plate 13 and the input shaft 26. A hydraulic pump 14 is provided on the input shaft 26 near the baffle plate 13 (see Figure 6 , Figure 7 ), the hydraulic pump 14 is composed of a pump body 14-1 and a plurality of pump nozzles 14-2. The pump body 14-1 is a hollow rotating body with small ends and a large middle. One end of the pump body 14-1 is inserted into the annular gap between the baffle 13 and the input shaft 26, and its end face is close to the side of the wedge block 41 and a gap is left.

[0053] The outer circumferential portion of the pump body 14 - 1 inserted into the baffle 13 has a plurality of annular grooves, the outer diameter of which is in clearance with the inner hole of the baffle 13 ; the inner hole of the baffle is provided with a plurality of axial grooves 14 - 3 evenly distributed around the circumference, the inner diameter of which is in clearance with the input shaft 26 .

[0054] The hole at the other end of the pump body 14 - 1 is tightly matched with the input shaft 26 , and is connected to the input shaft 26 by a pin 15 or a fastener, and is axially positioned by the shoulder of the input shaft 26 .

[0055] The pump body 14-1 is evenly provided with 2 to 6 pump nozzles 14-2 in the radial direction. The pump nozzle 14-2 is a pipe elbow close to 90 degrees, one end of which is vertically welded or threaded to the pump body 14-1, and the other end is outward and the pipe elbow direction is toward the direction of the input shaft 26. The maximum turning radius of the pump nozzle 14-2 is slightly smaller than the inner hole radius of the outer ring 10 at the corresponding position.

[0056] The hydraulic pump 14 connects the inner cavity of the pump body 14 with the outside through the pump nozzle 14-2 and the groove 14-3. The outer side of the outer ring end cover 16 is also coaxially connected with an oil slinger 18, which is a hollow rotating body and forms an annular cavity with the outer ring end cover 16. A plurality of axial small holes are evenly arranged near the inner cavity major diameter of the outer ring end cover 16, and the small holes connect the cavity where the hydraulic pump 14 is located and the cavity of the oil slinger 18.

[0057] The oil slinger 18 is also evenly provided with a number of notches on its outer circumference. A guide plate 25 is provided between the inner side of the box end cover 33 and the oil slinger 18 and close to the upper part of the box body 8. The guide plate 25 is a component composed of an upper plate 25-1, a baffle 25-2, and a lower plate 25-3. It is fixed to the box end cover 33 with screws 19. An oil filling cup 48 is provided on the upper part of the box body 8 corresponding to the upper plate 25-1. One side of the baffle 25-2 is close to the inner side of the box end cover 33, and a small gap is left between the other side and the end face of the oil slinger 18. The lower plate 25-3 is inserted obliquely downward into the inner cavity of the oil slinger 18 from the inner end face of the box end cover 33 and the gap between the oil slinger 18 and the input shaft 26.

[0058] During operation, a proper amount of oil 39 is injected into the box body 8. As long as the output shaft 1 rotates, the notch on the oil slinger 18 can swing the oil 39 from the bottom of the box body 8 to the upper part, and the oil 39 is blocked by the upper plate 25-1 and the baffle 25-2 of the guide plate 25 and flows into the inner cavity of the oil slinger 18 along the lower plate 25-3.

[0059] Due to the high-speed working condition, when the oil slinger 18 rotates at a high speed, the oil entering the oil slinger 18 forms an annular oil layer on the inner wall of the oil slinger 18 under the action of centrifugal force, and enters the cavity where the hydraulic pump 14 is located along the small holes on the outer ring end cover 16, forming an annular oil layer on the inner wall of the outer ring 10 and rotating at the same speed as the outer ring 14. As the oil layer thickens, the pump nozzle 14-2 will be immersed in the oil layer.

[0060] When the clutch is in the overrunning state, since the inlet of the pump nozzle 14-2 is opposite to the movement direction of the oil layer, the oil enters the inner cavity of the pump body 14-1, accumulates to a certain pressure, and is ejected from the axial groove 14-3 on the side of the wedge block, flows along the input shaft 26 through the joint of the wedge block 41, and forms an oil layer covering the surface of the input shaft 26. The wedge block 41 rotates together with the outer ring 10, so the lower working surface of the wedge block 41 (that is, the surface in contact with the input shaft) passes through the oil layer at high speed and is lifted up by the oil layer and leaves the surface of the input shaft 26, reaching a non-contact overrunning state without wear and heat, and the clutch can achieve high-speed overrunning.

[0061] The oil flowing through the wedge block 41 flows back from the hole in the center of the input shaft 26, and finally returns to the cavity of the oil slinger 18 along the radial holes arranged at the corresponding position of the oil slinger 18, and enters the circulation again. The notch of the oil slinger 18 continuously throws up the oil 39, and continuously replenishes it to the inner cavity of the oil slinger 18 along the guide plate 25.

[0062] When the output shaft 1 overtakes at high speed, the relative movement between the wedge block 41 and the input shaft 26 and the relative movement between the oil layer and the pump nozzle 14-2 will form a torque on the input shaft 26. The spring force of the annular tension spring 21 is adjusted so that the braking force of the brake assembly on the input shaft 26 is slightly larger than the torque. The input shaft 26 remains stationary to protect the drive motor and other equipment. Also, when overtaking at high speed, the pump nozzle 14-2 and the oil layer are kept in relative motion with a high speed difference, so that the function of the hydraulic pump 14 is reliably realized.

[0063] When the input shaft 26 has power input, the braking force is so small that it can be almost ignored. The centrifugal block 32 will move toward the outer periphery of the brake disc 29, loosen the sealing cover 24, lose the clamping force, and the brake assembly will operate without heat and wear. When the input shaft 26 gradually accelerates, the speed difference between the output shaft 1 and the input shaft 26 decreases, the relative speed between the oil layer and the pump nozzle 14-2 decreases, the oil entering the pump body 14-1 decreases, and the oil lifting force on the wedge block 41 gradually decreases. The wedge block 41 resumes contact with the surface of the input shaft 26 under the action of the support spring 42. At the moment when the input shaft 26 exceeds the speed of the output shaft 1, the clutch is wedged to transmit torque, thereby achieving engagement at high speed.

Claims

1. A high-speed overrunning clutch, comprising a housing and a clutch, wherein the housing is provided with bearings (6) at both ends and has a cavity structure in the middle, wherein the cavity structure accommodates the housing of the clutch rotary structure, and wherein: The box body comprises a box body (8), a fan (3) is arranged on one side of the box body (8), and a box body end cover (33) is arranged on the other side, a protective cover (46) is arranged outside the fan (3) and the box body end cover (33), and a sealing cover (24) and a centrifugal brake assembly composed of a plurality of centrifugal blocks (32), an annular tension spring (21), and a brake disc (29) are also arranged outside the box body end cover (33); The clutch comprises an output shaft (1), an input shaft (26), an outer ring (10), and an outer ring end cover (16); One end of the output shaft (1) extends from the side of the box end cover (33) into the box body (8), and the shaft end extends from the inner hole of the bearing (6) to the outside of the box body (8) and is supported by the bearing (6); a threaded sealing cover (4) is provided on the outer side of the bearing (6), and the inner hole of the threaded sealing cover (4) is provided with an internal thread and a vent hole, the threaded sealing cover (4) and the output shaft (1) are clearance-matched, and the vent hole is provided at the upper part of the inner hole of the threaded sealing cover (4); A plurality of wedge blocks (41) are arranged in an annular cavity formed between the outer ring (10) and the input shaft (26); a support spring (42) is passed through the middle of the wedge block (41); the support spring (42) causes the wedge block (41) and the inner wall of the outer ring (10) to be tensioned and rotate with the outer ring (10); the height of the wedge block (41) is greater than the distance of the radial gap between the outer ring (10) and the input shaft (26); and the wedge block (41) is in a diagonal support state; The end surface of the outer ring (10) is further provided with a baffle (13), an annular gap is provided between the baffle (13) and the input shaft (26) in the radial direction, and a hydraulic pump (14) is provided on the input shaft (26) close to the baffle (13); The outer side of the outer ring end cover (16) is also coaxially connected to an oil slinger ring (18), and the oil slinger ring (18) is also evenly provided with a plurality of notches on its outer circumference. The oil slinger ring (18) is a hollow rotating body, and an annular cavity is formed between the oil slinger ring (18) and the outer ring end cover (16). The outer ring end cover (16) is provided with a plurality of axial small holes near the inner cavity of the oil slinger ring (18), and the small holes are connected to the cavity where the hydraulic pump (14) is located and the cavity where the oil slinger ring (18) is located. A guide plate (25) and an oil filling cup (48) are also provided on the upper part of the box body (8) and between the inner side of the box body end cover (33) and the oil slinger (18); The guide plate (25) is a component consisting of an upper plate, a baffle plate, and a lower plate, and is fixed to the box end cover (33) by screws; an oil filling cup (48) is provided on the upper part of the box body (8) corresponding to the upper plate; one side of the baffle plate is close to the inner side of the box end cover (33), and the other side is in clearance fit with the end face of the oil slinger (18); the lower plate is inserted into the inner cavity of the oil slinger (18) from the inner end face of the box end cover (33) and obliquely downward from the gap between the oil slinger (18) and the input shaft (26); The hydraulic pump (14) comprises a pump body and a plurality of pump nozzles. The pump body is a hollow rotating body with small ends and a large middle. One end of the pump body is inserted into the annular gap between the baffle (13) and the input shaft (26). The outer circumference of the pump body inserted into the baffle (13) has a plurality of annular grooves, and the outer diameter of the annular grooves matches the inner hole gap of the baffle (13). The hole at the other end of the pump body is matched with the input shaft (26) for installation and is connected to the input shaft (26) by a fastener.

2. A high-speed overrunning clutch according to claim 1, characterized in that: The brake disc (29) is fastened to an input shaft (26) extending out of the box body (8) by a connecting piece. A plurality of blocks (22) are arranged inside the brake disc (29) to divide the inner circumference of the brake disc (29) into a plurality of parts. A centrifugal block (32) is arranged between adjacent blocks (22). The block (22) and the centrifugal block (32) arranged therebetween form a circular ring structure. Grooves are arranged on both sides of the circular ring structure. An annular tension spring (21) connected end to end is arranged inside the groove. The annular tension spring (21) enables the centrifugal block (32) to move toward the input shaft (26) and to hold a sealing cover (24) fixed on the outside of the box body end cover (33).

3. A high-speed overrunning clutch according to claim 1, characterized in that: One end of the outer ring (10) is connected to the output shaft (1) via a flange, and the other end is connected to the outer ring end cover (16); one end of the input shaft (26) is inserted into the outer ring (10), and the other end passes through the outer ring end cover (16) and is installed opposite to the output shaft (1), and extends out of the box body (8).

4. A high-speed overrunning clutch according to claim 1, characterized in that: The center of the cross section of the wedge block (41) is circular, and adjacent wedge blocks (41) are arranged with a slight gap between each other, and each of them rotates around the center circle axis.

5. A high-speed overrunning clutch according to claim 1, characterized in that: The pump body is evenly provided with 2 to 6 pump nozzles in the radial direction, one end of the pump nozzle is welded or threaded perpendicular to the pump body, and the other end is bent in the direction of the input shaft (26), and the pump nozzle connects the inner cavity of the pump body with the outside.

6. A high-speed overrunning clutch according to claim 1, characterized in that: The input shaft (26) is a multi-step stepped shaft, one end of which is centrally punched with a hole connected to a radial hole on the input shaft, and the position of the radial hole is aligned with the oil slinger (18).

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