CN118309779B - Overrunning damping wheel with overload protection - Google Patents
Overrunning damping wheel with overload protection Download PDFInfo
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- CN118309779B CN118309779B CN202410745800.XA CN202410745800A CN118309779B CN 118309779 B CN118309779 B CN 118309779B CN 202410745800 A CN202410745800 A CN 202410745800A CN 118309779 B CN118309779 B CN 118309779B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
- F16H2055/366—Pulleys with means providing resilience or vibration damping
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention discloses an overrun damping wheel with overload protection, and aims to solve the problem that a torsion spring is easy to fail due to the fact that the damping belt wheel of an automobile generator is influenced by frequent change of torque for a long time in the process of transmitting torque in the prior art. The invention solves the technical problems by the following technical proposal: comprising the following steps: the belt pulley, the shaft core and the torque transmission assembly comprise a connecting ring, a clutch coil spring and a load torsion spring which are all sleeved on the outer side of the shaft core; the belt pulley is provided with a belt pulley hole, the shaft core is arranged in the belt pulley hole in a penetrating way, and the belt pulley hole and the outer wall of the shaft core are matched to form a first annular cavity and a second annular cavity; the clutch coil spring and the load torsion spring are both provided with one end which is abutted with the connecting ring, one end which is far away from the connecting ring is abutted with the spring seat on the shaft core, and one end which is far away from the connecting ring is abutted with the belt pulley.
Description
Technical Field
The invention relates to the technical field of generator belt pulleys, in particular to an overrunning damping wheel with overload protection.
Background
Automobile generators are widely driven by accessory belts in automobile design, and are generally driven by connecting a fixed belt pulley, an overrunning belt pulley and an overrunning vibration isolation wheel with the generator. When the whole vehicle needs a generator to generate electricity, if a rigid belt wheel is adopted, the impact vibration of the generator on a belt driving system under the dual actions of the large torque required by the motor and the self inertia moment of the motor cannot be slowed down; if the overrunning damping wheel is adopted, the internal parts are not protected or only partially protected due to overlarge torque under certain working conditions, so that the internal parts are easy to damage and lose efficacy. When the engine is decelerated, the inertia moment of the generator acts, so that the generator is converted into a driving wheel in an accessory driving system, the tightness relation of the belt is converted, and the requirement on the tension of the system is high, so that the overrunning action of the overrunning belt wheel or the overrunning damping wheel is required to isolate the influence of the generator on the belt transmission system. When the existing overrunning damping wheel design transmits large torque, the existing overrunning damping wheel design cannot completely protect parts such as an internal clutch and a spring due to the limitation of the structural design, and the whole failure is easy to occur, so that the generator cannot generate electricity. There is therefore a need for an improved structural design for effective overload protection of the internal components of an overrunning damper wheel.
The invention discloses an overrunning damping belt pulley of a combined torsion spring type automobile generator, which mainly realizes load transmission through a torque ring and absorbs torsional vibration and moment impact transmitted by the belt pulley through deformation of the torsion spring ring when the belt pulley is used, so that noise generated in the belt running process can be reduced; but in the process of torque ring transmission load, because torque ring is long-time and belt pulley rub, the torque ring is easy to take place deformation inefficacy after the time is long, especially when the moment of torsion suddenly increases, when torque ring and belt pulley contact this moment, the frictional force contact of torque ring and belt pulley is too big for the problem that the torque ring can take place deformation inefficacy more easily, thereby the problem that the generator can't generate electricity appears.
Chinese patent publication No. CN106687706a, publication No. 2019, 1/1, entitled a decoupler, in which the torque transmission path is mainly transmitted to the one-way clutch through the wheel, then to the carrier through the one-way clutch, then to the isolation spring through the carrier, and finally to the hub through the isolation spring. In the above application, there are several disadvantages: (1) The torque transmission path can only be transmitted to the hub through the one-way clutch, the bearing piece and the isolation spring in sequence, so that the one-way clutch and the inner surface of the wheel are required to transmit torque, and friction is repeatedly generated, the one-way clutch and the inner surface of the wheel are required to be subjected to special treatment, the manufacturing cost is increased, and failure is easy to occur; (2) In the torque transmission process, the one-way clutch and the bearing piece need to bear all the torque, so that the one-way clutch and the bearing piece need to be subjected to special processing treatment, the manufacturing cost is increased, and the problem of failure is easy to occur; (3) The torque can be transmitted only through the one-way clutch and the isolation spring, only two-stage rigidity is achieved, and the conditions such as vibration and the like are easy to occur in the process of gradually increasing the torque; (4) The one-way clutch and the isolation spring are provided with an overlapped part in the axial direction, a sleeve is arranged between the one-way clutch and the isolation sleeve, the sleeve adopts a spiral structure, and when high torque is transmitted, the one-way clutch, the isolation spring and the sleeve are abutted, so that tangential friction force is applied to the surface of the one-way clutch, the adhesive force between the one-way clutch and a wheel is weakened or counteracted, the bearing capacity of the clutch is weakened or destroyed, and even the slipping failure of the clutch is caused; even when the radial abutting force is high enough, the one-way clutch, the isolation spring and the sleeve are mutually extruded to be mutually embedded and entangled, so that the collapse failure is caused.
Disclosure of Invention
The invention solves the problem that the clutch coil spring is influenced by frequent change of torque for a long time in the process of transmitting torque of the belt pulley of the automobile generator in the prior art, so that the clutch is easy to fail, provides the overrunning damping wheel with overload protection, according to the torque, the path from the pulley to the shaft core can be automatically adjusted, so that the problems of failure of parts such as a clutch, a torsion spring and the like caused by overlarge torque can be avoided, and the overall service life is prolonged.
In order to solve the technical problems, the invention adopts the following technical scheme: an overrunning shock absorbing wheel with overload protection, comprising: the belt pulley, the shaft core and the torque transmission assembly comprise a connecting ring, a clutch coil spring and a load torsion spring which are all sleeved on the outer side of the shaft core;
The belt pulley is provided with a belt pulley hole, the shaft core is arranged in the belt pulley hole in a penetrating way, the belt pulley hole and the outer wall of the shaft core are matched to form a first annular cavity and a second annular cavity, the first annular cavity is communicated with the second annular cavity, the clutch coil spring is arranged in the first annular cavity, and the load torsion spring is arranged in the second annular cavity;
One end of the clutch coil spring is abutted with the connecting ring, one end of the load coil spring is abutted with a spring seat on the shaft core, and the other end of the clutch coil spring is abutted with the belt pulley;
The clutch coil spring is always contacted with the radial direction of the first annular cavity, and the number of turns of the load torsion spring contacted with the second annular cavity changes along with the change of the transmitted torque;
The torque of the clutch coil spring energizes the load torsion spring so as to change the contact state of the load torsion spring and the second annular cavity; when the load torsion spring is in radial contact with the second annular cavity, part of torque of the belt pulley is directly transmitted to the shaft core through the load torsion spring, and the rest of torque of the belt pulley is sequentially transmitted to the shaft core through the clutch coil spring, the connecting ring and the load torsion spring.
Under the condition of low load, the transmission path of the torque is that the belt pulley transmits the torque to the clutch coil spring, the clutch coil spring transmits the torque to the load torsion spring through the connecting ring, and the load torsion spring transmits the torque to the shaft core through the spring seat.
Under the high load condition, the clutch coil spring is used for accumulating enough torque, the torque is transmitted to the load torsion spring through the connecting ring, the load torsion spring is outwards expanded, the load torsion spring is abutted against the side wall of the second annular cavity, the torque can be directly transmitted to the load torsion spring from the belt pulley, and then the torque is transmitted to the shaft core through the spring seat by the load torsion spring. That is, there are two transfer paths under high load. The first is the same as the low load transfer path; the second transmission path is that torque can be directly transmitted from the belt pulley to the load torsion spring, and then the load torsion spring transmits the torque to the shaft core through the spring seat.
Therefore, the invention can automatically adjust the path of the belt pulley for transmitting the torque to the shaft core according to the torque, so that the torsion spring can not fail due to overlarge torque for a long time, thereby prolonging the service life of the whole body.
Preferably, the connecting ring is concentrically provided with two unidirectional ring seats, and the clutch coil spring and the load torsion spring are respectively abutted against the two unidirectional ring seats.
The connecting ring enables torque from the clutch wrap spring to be transferred to the load torsion spring.
Preferably, the diameter of the loaded torsion spring increases gradually from one end to the other.
The load torsion spring is arranged to be conical, so that the engagement length of the load torsion spring and the inner wall of the belt pulley is correspondingly increased along with the increase of torque, and the adhesion capability is improved; and the work turns of the load torsion spring are reduced, so that the torsional rigidity of the load torsion spring is continuously increased, and effective buffering during heavy load is realized.
Preferably, the diameter of the second annular cavity increases gradually from one end to the other.
The engagement length of the load torsion spring and the inner wall of the belt pulley is correspondingly increased along with the increase of the torque, so that the adhesion capability is improved; and the work turns of the load torsion spring are reduced, so that the torsional rigidity of the load torsion spring is continuously increased, and effective buffering during heavy load is realized.
Preferably, an end cover is arranged at one end part of the shaft core, the spring seat is arranged on the end cover, and the end part of the load torsion spring, which is far away from the connecting ring, is abutted against the spring seat on the end cover.
The spring seat is arranged on the end cover, so that torque of the load torsion spring can be smoothly transmitted to the shaft core through the end cover.
Preferably, the outer side wall of the end cover is provided with an annular groove, a bushing is arranged in the annular groove, and the outer side wall of the bushing is abutted with the belt wheel hole.
The bushing enables relative rotation between the end cap and the pulley.
Preferably, a bearing is abutted between the outer side wall of one end of the shaft core away from the end cover and the inner side wall of the belt wheel hole.
The function of the bearing is similar to that of the bushing, and the shaft core can rotate freely relative to the belt pulley.
Preferably, a gasket ring is arranged on the end face, close to the end cover, of the bearing, and the connecting ring abuts against the gasket ring.
The gasket ring is mounted to the outer end of the connecting ring to prevent direct contact between the connecting ring and the bearing, resulting in excessive wear.
Preferably, a sealing cover is arranged at one end of the pulley hole close to the end cover.
The sealing cover is arranged on the belt pulley to prevent foreign matters from entering the belt pulley and prevent internal grease from flowing out.
Preferably, the shaft core is internally provided with a mounting hole, and the opening direction of the mounting hole is opposite to that of the sealing cover.
The setting of mounting hole makes for can conveniently install with the pivot of generator.
Compared with the prior art, the invention has the beneficial effects that:
(1) Under high load, there are two transfer paths compared to low load, so that under high load, through the combination of the load torsion spring and the inner side wall of the pulley, a primary torque load transferring channel is formed, thereby protecting the clutch coil spring and the load torsion spring. Therefore, the invention can automatically adjust the path of the belt pulley for transmitting the torque to the shaft core according to the torque, so that the torsion spring can not fail due to overlarge torque for a long time, thereby prolonging the service life of the whole body.
(2) The engine causes acceleration of the pulley at the time of acceleration or at the time of high load of the generator, so that the torque of the pulley increases. Firstly, the contact of the inner side wall of the belt pulley and the clutch coil spring transmits low torque, and along with the gradual increase of the torque, the torque is directly transmitted through the load torsion spring, so that the torque can be transmitted from low to high, the contact of the inner side wall of the belt pulley and the load torsion spring can be reduced, the load torsion spring and the inner wall of the belt pulley can be greatly worn due to the sudden contact of the load torsion spring under the condition of large torque, and the service life of the load torsion spring is reduced. That is, the torque transmission device can adapt to the transmission of torque in a larger range, so that the torque transmission device can be more stable, and noise and vibration can be effectively reduced.
(3) The clutch coil spring is only used for controlling whether the load torsion spring is contacted with the wall of the second annular cavity or not, and does not transmit main torque, so that the clutch coil spring is always subjected to smaller torque, and only about 5N/m torque is needed to be born, the service life of the clutch coil spring can be kept high, and the overall service life is prolonged.
(4) The clutch coil spring is generally about 4 circles, the clutch coil spring and the connecting ring can be designed in a lightweight mode, the precision requirement is low, and the clutch coil spring is easy to manufacture and not easy to damage. Compared with the one-way clutch in the prior art (CN 106687706A), the one-way clutch is generally about 9 circles, and the one-way clutch and the bearing piece are required to be designed with high strength and high precision, so that the one-way clutch is not easy to manufacture and damage.
(5) In the application, under the condition of high load, the torque transmission path is mainly transmitted through the load torsion spring, so that special treatment is not needed between the clutch coil spring and the belt pulley, the manufacturing process is reduced, and the manufacturing cost is reduced.
(6) The clutch coil spring and the load torsion spring are not contacted in the radial direction no matter how much torque is applied, and the clutch coil spring and the load torsion spring are acted in the respective cavities, so that the situation that the clutch coil spring and the load torsion spring are mutually embedded and entangled due to mutual extrusion to cause breakdown failure is fundamentally avoided.
(7) The rigidity of the load torsion spring is improved along with the increase of the moment, so that the damping effect can be improved, the damping function is achieved, and the whole operation is more stable.
(8) The belt pulley is connected together through clutch spring and load torsional spring, and the belt pulley moment of torsion is transmitted to the axle core through clutch spring, go-between, load torsional spring, utilizes the torsional elasticity of torsional spring, also can reduce impact and the vibration that produces in the load transmission process.
(9) When the engine is decelerated, the belt pulley is decelerated, and the generator and the shaft core can continue to operate at a higher rotating speed by utilizing the unidirectional disengagement characteristic of the torsion spring.
Drawings
Fig. 1 is a perspective view of the present invention.
Fig. 2 is a cross-sectional view of the present invention.
Fig. 3 is an exploded view of the present invention.
Fig. 4 is a perspective view of the connecting ring of the present invention.
Fig. 5 is a perspective view of the bushing in embodiment 1 and embodiment 2 of the present invention.
Fig. 6 is a cross-sectional view in embodiment 2 of the present invention.
Fig. 7 is a cross-sectional view in embodiment 3 of the present invention.
Fig. 8 is a cross-sectional view taken along the direction A-A in fig. 7.
Fig. 9 is a cross-sectional view in embodiment 4 of the present invention.
Fig. 10 is a torque characteristic diagram of the present invention.
In the figure: 1. the belt pulley, 11, the first annular cavity, 12, the second annular cavity, 13, the transmission annular wall, 131, the abutting ring, 14, the limiting ring, 141 and the arc-shaped groove;
2. the shaft core, 21, the end cover, 22, the annular groove, 23 and the mounting hole;
3. The torque transmission assembly 31, the connecting ring 311, the unidirectional inner ring seat 312, the unidirectional outer ring seat 313, the synchronous protruding shaft 32, the clutch coil spring 33 and the load torsion spring;
4. A spring seat;
5. bushing 6, bearing 7, gasket ring 8, sealed lid.
Detailed Description
The technical scheme of the invention is further specifically described by the following specific embodiments with reference to the accompanying drawings:
example 1: referring to fig. 1 to 5, an overrunning damper wheel with overload protection, comprising: the pulley 1, the axle core 2 and the torque transmission assembly 3, the torque transmission assembly 3 includes the go-between 31, clutch spring 32 and load torsional spring 33 all cover and establish in the axle core 2 outside, and go-between 31 can rotate around axle core 2 freedom, and the rigidity of load torsional spring 33 is greater than the rigidity of clutch spring 32.
The belt pulley 1 is internally provided with a belt pulley hole, the shaft core 2 is arranged in the belt pulley hole in a penetrating way, the belt pulley hole and the outer wall of the shaft core 2 are matched to form a first annular cavity 11 and a second annular cavity 12, the first annular cavity 11 and the second annular cavity 12 are communicated, the first annular cavity 11 and the second annular cavity 12 are coaxially arranged, the clutch coil spring 32 is arranged in the first annular cavity 11, and the load torsion spring 33 is arranged in the second annular cavity 12; the axial length of the second annular chamber 12 is greater than the axial length of the first annular chamber 11, and the first annular chamber 11 in this embodiment is provided on the side wall of the second annular chamber 12 so that the diameter of the first annular chamber 11 is greater than that of the second annular chamber 12.
In this embodiment, two unidirectional ring seats are concentrically arranged on the connection ring 31, the two unidirectional ring seats are respectively a unidirectional inner ring seat 311 and a unidirectional outer ring seat 312, the clutch coil spring 32 is abutted with the unidirectional outer ring seat 312, and the load torsion spring 33 is abutted with the unidirectional inner ring seat 311. Both the clutch coil spring 32 and the load torsion spring 33 have one end abutting the connection ring 31.
The connecting ring 31 is disposed at the overlapping end portions of the first annular chamber 11 and the second annular chamber 12, so that the first annular chamber 11 and the second annular chamber 12 form a space independent of each other. Thereby preventing the clutch coil spring 32 and the load torsion spring 33 from coming into contact.
The load torsion spring 33 and the clutch coil spring 32 are rectangular in cross section, so that the contact area with the inner wall of the pulley 1 can be increased.
One end of the clutch coil spring 32 remote from the connection ring 31 abuts the pulley 1. The end of the clutch coil spring 32 abuts against the pulley 1, and rotation of the clutch coil spring 32 in the circumferential direction near the end of the pulley 1 can be restricted. One end of the load torsion spring 33, which is far away from the connecting ring 31, is abutted against the spring seat 4 on the shaft core 2, and the spring seat 4 can limit the rotation of the end part of the load torsion spring 33 in the circumferential direction. The end of the shaft core 2 is provided with an end cover 21, in this embodiment, the spring seat 4 is disposed on the end cover 21, the spring seat 4 and the end cover 21 are integrally formed, and the end of the load torsion spring 33 far away from the connecting ring 31 is abutted against the spring seat 4 on the end cover 21.
The outer side wall of the end cover 21 is provided with an annular groove 22, a bushing 5 is arranged in the annular groove 22, and the outer side wall of the bushing 5 is abutted against the inner side wall of the belt wheel hole. Bushing 5 allows relative rotation between end cap 21 and pulley 1. A bearing 6 is abutted between the outer side wall of the end of the shaft core 2 away from the end cover 21 and the inner side wall of the pulley hole. The function of the bearing 6 is similar to that of the bushing 5, allowing the free rotation of the shaft core 2 with respect to the pulley 1.
Since the connecting ring 31 is disposed at one end near the bearing 6 in the present embodiment, so that the connecting ring 31 abuts against the end face of the bearing 6, in order to reduce the influence on the bearing 6, in the present embodiment, the gasket ring 7 is disposed on the end face of the bearing 6 near the end cap 21, that is, the gasket ring 7 is disposed on the end face of the bearing 6 near the connecting ring 31, and the connecting ring 31 abuts against the gasket ring 7.
The end of the pulley hole near the end cap 21 is provided with a sealing cap 8. The sealing cover 8 can allow dust to enter the pulley hole while preventing the grease inside from flowing out.
The shaft core 2 is internally provided with a mounting hole 23, and the opening direction of the mounting hole 23 is opposite to that of the sealing cover 8. The mounting hole 23 is used for connecting with the rotating shaft of the generator.
In addition, referring to fig. 2, the diameter of the second annular chamber 12 in this embodiment gradually increases from one end to the other end, and the diameters of the clutch coil spring 32 and the load torsion spring 33 are unchanged in the axial direction, that is, the clutch coil spring 32 and the load torsion spring 33 are both cylindrical. Such that the inner side wall of the second annular chamber 12 forms a conical structure that may be tapered in opening. In addition, the inner wall of the combination with the load torsion spring 33 is designed to be tapered, so that the engagement length of the load torsion spring 33 and the inner wall of the pulley 1 increases correspondingly with the increase of torque, to improve the adhesion capability; and the reduction of the work turns of the load torsion spring 33 causes the torsional rigidity of the load torsion spring 33 to continuously rise, so as to realize effective buffering under heavy load.
The installation process of this embodiment is as follows: one ends of both the clutch coil spring 32 and the load coil spring 33 are fitted with the connection ring 31 so that the torque of the clutch coil spring 32 can be transmitted to the load coil spring 33 through the connection ring 31. The other end of the load torsion spring 33 remote from the connecting ring 31 is placed on the spring seat 4 of the spindle 2, so that torque can be transmitted to the spindle 2 through the load torsion spring 33. The spacer ring 7 is mounted to the outer end of the connection ring 31 to prevent the connection ring 31 from directly contacting the bearing 6, causing excessive wear. The bushing 5 is arranged in an annular groove 22 at the end cover 21 of the shaft core 2, so that the shaft core 2 is prevented from being in direct contact with the inner wall of the belt pulley 1, and the function of isolating and self-lubricating the bearing is achieved. The clutch coil spring 32 is tightened by a tool, the internal part is integrally placed into the pulley hole of the pulley 1, the clutch coil spring 32 is in an interference fit design with the first annular cavity 11 in a natural state, so that the tool hand is loosened, the outer diameter of the clutch coil spring 32 is expanded, the clutch coil spring 32 is always combined with the inner wall of the first annular cavity 11, and a certain torque load can be transmitted. Grease for lubrication is injected into the clutch coil spring 32, so that abrasion of the clutch coil spring 32 and the inner wall of the first annular cavity 11 is reduced, lubrication is increased when the load torsion spring 33 and the inner wall of the first annular cavity 11 are combined, and abrasion during separation and combination is reduced. And a bearing 6 is arranged to ensure that the belt pulley 1 and the shaft core 2 can rotate relatively, so that the installation of parts is completed. After the invention is installed on the generator, the sealing cover 8 is installed on the belt pulley 1 to prevent foreign matters from entering the inside of the belt pulley 1 and prevent the grease in the inside from flowing out.
The working principle in this embodiment is divided into two cases of high load and low load, and the two working conditions are discussed below, respectively.
(1) In a low load condition, the clutch coil spring 32 abuts against the side wall of the first annular cavity 11, the torque transmission path is that the belt pulley 1 transmits the torque to the clutch coil spring 32, the clutch coil spring 32 transmits the torque to the load torsion spring 33 through the connecting ring 31, and the load torsion spring 33 transmits the torque to the shaft core 2 through the spring seat 4. Because the torque at this time is small, the load torsion spring 33 is not greatly deformed, and thus the load torsion spring 33 does not transmit torque in contact with the inner side wall of the pulley 1. As shown in the OA section curve in fig. 10, the load torsion spring 33 at this time is not in contact with the inner side wall of the second annular chamber 12, and the torque of the pulley 1 is transmitted to the shaft core 2 through the clutch coil spring 32, the connecting ring 31 and the load torsion spring 33 in this order, and the load torsion spring 33 and the clutch coil spring 32 participate in vibration reduction at the same time.
(2) Under high load conditions, the clutch coil spring 32 accumulates enough torque to be transmitted to the load torsion spring 33 through the connecting ring 31, so that the load torsion spring 33 expands outwards, the load torsion spring 33 abuts against the side wall of the second annular cavity 12, so that the torque can be directly transmitted from the pulley 1 to the load torsion spring 33, and then the load torsion spring 33 transmits the torque to the shaft core 2 through the spring seat 4. That is, there are two transfer paths under high load. The first is the same as the transmission path of the low load, namely, the pulley 1 transmits to the clutch coil spring 32, the clutch coil spring 32 transmits torque to the load torsion spring 33 through the connecting ring 31, and the load torsion spring 33 transmits torque to the shaft core 2 through the spring seat 4; the second transmission path is that torque can be directly transmitted from the pulley 1 to the load torsion spring 33, after which the load torsion spring 33 transmits torque to the spindle 2 through the spring seat 4. As shown in an AB section curve in fig. 10, the load torsion spring 33 receives the torque of the clutch coil spring 32, the axial length of the load torsion spring 33 abutting against the second annular cavity 12 gradually increases with the increase of the torque, at this time, a part of the outer side wall of the load torsion spring 33 abuts against the second annular cavity 12, the load torsion spring 33 does not have a vibration damping effect on the part abutting against the second annular cavity 12, and the load torque of the clutch coil spring 32 is always maintained at the point a; after the load torsion spring 33 is fully abutted against the inner wall of the second annular cavity 12, the curve at this time is at BC, the load torsion spring 33 is fully used for transmitting torque, and the load torque of the clutch coil spring 32 is always maintained at the point a.
The invention has the beneficial effects that: (1) The engine causes acceleration of the pulley 1 at the time of acceleration or at the time of high load of the generator, so that the torque increases. Firstly, the inner side wall of the belt pulley 1 is contacted with the clutch coil spring 32 to transmit low torque, and the torque is transmitted through the load torsion spring 33 along with the gradual increase of the torque, so that the torque can be transmitted from low to high, the sudden contact with the inner side wall of the belt pulley 1 under the condition of large torque of the load torsion spring 33 can be reduced, the load torsion spring 33 and the inner wall of the belt pulley 1 are greatly worn, and the service life of the load torsion spring 33 is shortened. That is, the torque transmission device can adapt to the transmission of torque in a larger range, so that the torque transmission device can be more stable, and noise and vibration can be effectively reduced.
(2) In the case of high load, there are two transmission paths compared to low load, so that a channel for mainly transmitting torque load is formed by the combination of the load torsion spring 33 and the inner side wall of the pulley 1 under high load, thereby protecting the clutch coil spring 32 and the load torsion spring 33 (as shown in fig. 10, the clutch coil spring 32 load torque always maintains the a point size).
(3) When the engine is decelerated, the deceleration of the belt pulley 1 is caused, and the generator and the shaft core 2 can continue to operate at a higher rotating speed by utilizing the unidirectional disengagement characteristic of the torsion spring.
(4) The pulley 1 is connected together through the clutch coil spring 32 and the load torsion spring 33, and the pulley 1 torque is transmitted to the axle core 2 through the clutch coil spring 32, the connecting ring 31 and the load torsion spring 33, and the torsional elasticity of the torsion spring is utilized to reduce the impact and vibration generated in the load transmission process.
Example 2: referring to fig. 4 and 6, the present embodiment is similar to the structure of embodiment 1, except that the second annular chamber 12 and the load torsion spring 33 are mainly different in size, the first annular chamber 11 and the second annular chamber 12 are both cylindrical in structure, and the diameter of the load torsion spring 33 is gradually increased from one end toward the other end, so that the load torsion spring 33 forms a conical shape with an opening gradually increased. By providing the load torsion spring 33 in a tapered shape, the engagement length of the load torsion spring 33 and the inner wall of the pulley 1 is increased correspondingly with an increase in torque, so as to improve the adhesion ability; and the reduction of the work turns of the load torsion spring 33 causes the torsional rigidity of the load torsion spring 33 to continuously rise, so as to realize effective buffering under heavy load.
Example 3: referring to fig. 4, 7 and 8, an overrunning damper wheel with overload protection, comprising: the pulley 1, the axle core 2 and the torque transmission assembly 3, the torque transmission assembly 3 includes the go-between 31, clutch spring 32 and load torsional spring 33 all cover and establish in the axle core 2 outside, and go-between 31 can rotate around axle core 2 freedom, and the rigidity of load torsional spring 33 is greater than the rigidity of clutch spring 32.
The belt pulley 1 is internally provided with a belt pulley hole, the shaft core 2 is arranged in the belt pulley hole in a penetrating way, the belt pulley hole and the outer wall of the shaft core 2 are matched to form a first annular cavity 11 and a second annular cavity 12, the first annular cavity 11 and the second annular cavity 12 are communicated, the first annular cavity 11 and the second annular cavity 12 are coaxially arranged, the clutch coil spring 32 is arranged in the first annular cavity 11, and the load torsion spring 33 is arranged in the second annular cavity 12; the axial length of the second annular chamber 12 is greater than the axial length of the first annular chamber 11. The first annular chamber 11 in this embodiment is disposed within the sidewall of the second annular chamber 12, the diameter of the first annular chamber 11 being greater than the diameter of the second annular chamber 12.
In this embodiment, two unidirectional ring seats are concentrically arranged on the connection ring 31, the two unidirectional ring seats are respectively a unidirectional inner ring seat 311 and a unidirectional outer ring seat 312, the load torsion spring 33 is abutted with the unidirectional inner ring seat 311 of the connection ring 31, and the clutch coil spring 32 is abutted with the unidirectional outer ring seat 312 of the connection ring 31. Both the clutch coil spring 32 and the load torsion spring 33 have one end abutting the connection ring 31.
The load torsion spring 33 and the clutch coil spring 32 are rectangular in cross section, so that the contact area with the inner wall of the pulley 1 can be increased.
One end of the clutch coil spring 32 away from the connection ring 31 abuts against the pulley 1, and the other end of the clutch coil spring 32 abuts against the end of the pulley 1 abutting against the first annular chamber 11, so that rotation of the clutch coil spring 32 in the circumferential direction near one end of the pulley 1 can be restricted. The load torsion spring 33 is abutted against the spring seat 4 on the shaft core 2 at one end far away from the connecting ring 31, and the spring seat 4 in the embodiment is arranged on the outer side wall of the shaft core 2, and the spring seat 4 and the shaft core 2 are integrally formed. The spring seat 4 and the spindle 2 are integrally formed, and the spring seat 4 can restrict rotation of the end portion of the load torsion spring 33 in the circumferential direction.
In this embodiment, a limiting ring 14 is disposed at the end of the shaft core 2 far away from the spring seat 4, and the limiting ring 14 and the shaft core 2 are integrally formed. The connecting ring 31 abuts against the stopper ring 14. In order to prevent the rotational speed of the shaft core 2 from being greater than that of the pulley 1, an arc groove 141 is provided in the stopper ring 14, and a synchronizing protruding shaft 313 provided in the arc groove 141 is provided in the connecting ring 31. In the normal torque range, when the connecting ring 31 rotates relative to the limiting ring 14, the synchronous protruding shaft 313 moves in the arc-shaped groove 141; when the rotation speed of the shaft core 2 exceeds a certain range, the synchronous protruding shaft 313 abuts against one end of the arc-shaped groove 141, so that the shaft core 2 can synchronously drive the connecting ring 31 to rotate. It should be noted that, although only one arc-shaped groove 141 is shown in the present embodiment, the number of the synchronous protruding shafts 313 and the number of the arc-shaped grooves 141 are adapted, respectively, although the number is not limited to one and may be plural.
The outer side wall of the limiting ring 14 is provided with an annular groove 22, a bushing 5 is arranged in the annular groove 22, and the outer side wall of the bushing 5 is abutted against the inner side wall of the belt wheel hole. The bushing 5 enables relative rotation between the shaft core 2 and the pulley 1. A bearing 6 is abutted between the outer side wall of one end of the shaft core 2 far away from the annular groove 22 and the inner side wall of the belt wheel hole. The function of the bearing 6 is similar to that of the bushing 5, allowing the free rotation of the shaft core 2 with respect to the pulley 1.
The end of the pulley bore adjacent the annular groove 22 is provided with a sealing cap 8. The sealing cover 8 can allow dust to enter the pulley hole while preventing the outflow of the internal grease.
The shaft core 2 is internally provided with a mounting hole 23, and the opening direction of the mounting hole 23 is opposite to that of the sealing cover 8. The mounting hole 23 is used for connecting with the rotating shaft of the generator.
The load torsion spring 33 may be provided in a shape having a large middle diameter and a small end diameter; the load torsion spring 33 may also be provided in a cylindrical shape of the same diameter; the second annular chamber 12 may be tapered or cylindrical. In the present embodiment, referring to fig. 7, the inside of the first and second annular chambers 11 and 12 is uniformly cylindrical, the clutch coil spring 32 is cylindrical, and the diameter of the load torsion spring 33 is gradually increased from one end toward the other end, so that the load torsion spring 33 forms a conical shape with an opening gradually increased. By providing the load torsion spring 33 in a tapered shape, the engagement length of the load torsion spring 33 and the inner wall of the pulley 1 is increased correspondingly with an increase in torque, so as to improve the adhesion ability; and the reduction of the work turns of the load torsion spring 33 causes the torsional rigidity of the load torsion spring 33 to continuously rise, so as to realize effective buffering under heavy load. The load torsion spring 33 may also be provided in a shape with a large middle diameter and a small end diameter; the load torsion spring 33 may also be provided in a cylindrical shape of the same diameter.
The installation process of this embodiment is as follows: one ends of both the clutch coil spring 32 and the load coil spring 33 are fitted with the connection ring 31 so that the torque of the clutch coil spring 32 can be transmitted to the load coil spring 33 through the connection ring 31. The other end of the load torsion spring 33 remote from the connecting ring 31 is placed on the spring seat 4 of the spindle 2, so that torque can be transmitted to the spindle 2 through the load torsion spring 33. The bushing 5 is installed in the annular groove 22 at the end of the shaft core 2, prevents the shaft core 2 from being in direct contact with the inner wall of the belt pulley 1, and plays a role in isolating and self-lubricating the bearing 6. The clutch coil spring 32 is expanded by a tool, the internal part is integrally placed into the pulley hole of the pulley 1, the clutch coil spring 32 is designed to be in interference fit with the first annular cavity 11 in a natural state, so that a tool hand is loosened, the outer diameter of the clutch coil spring 32 is expanded, and the clutch coil spring 32 and the inner wall of the first annular cavity 11 are combined together, so that a certain torque load can be transmitted. Grease for lubrication is injected into the clutch coil spring 32, so that abrasion of the clutch coil spring 32 and the inner wall of the first annular cavity 11 is reduced, lubrication is increased when the load torsion spring 33 and the inner wall of the second annular cavity 12 are combined, and abrasion during separation and combination is reduced. And a bearing 6 is arranged to ensure that the belt pulley 1 and the shaft core 2 can rotate relatively, so that the installation of parts is completed. After the invention is installed on the generator, the sealing cover 8 is installed on the belt pulley 1 to prevent foreign matters from entering the inside of the belt pulley 1 and prevent the grease in the inside from flowing out.
The working principle in this embodiment is divided into two cases of high load and low load, and the two working conditions are discussed below, respectively.
(1) In a low load condition, the clutch coil spring 32 abuts against the side wall of the first annular cavity 11, the torque transmission path is that the belt pulley 1 transmits the torque to the clutch coil spring 32, the clutch coil spring 32 transmits the torque to the load torsion spring 33 through the connecting ring 31, and the load torsion spring 33 transmits the torque to the shaft core 2 through the spring seat 4. Because the torque at this time is small, the load torsion spring 33 is not greatly deformed, and thus the load torsion spring 33 does not transmit torque in contact with the inner side wall of the pulley 1. As shown in the OA section curve in fig. 10, the load torsion spring 33 at this time is not in contact with the inner side wall of the second annular chamber 12, and the torque of the pulley 1 is transmitted to the shaft core 2 through the clutch coil spring 32, the connecting ring 31 and the load torsion spring 33 in this order, and the load torsion spring 33 and the clutch coil spring 32 participate in vibration reduction at the same time.
(2) Under high load conditions, the clutch coil spring 32 accumulates enough torque to be transmitted to the load torsion spring 33 through the connecting ring 31, so that the load torsion spring 33 expands outwards, the load torsion spring 33 abuts against the side wall of the second annular cavity 12, so that the torque can be directly transmitted from the pulley 1 to the load torsion spring 33, and then the load torsion spring 33 transmits the torque to the shaft core 2 through the spring seat 4. That is, there are two transfer paths under high load. The first is the same as the transmission path of the low load, namely, the pulley 1 transmits to the clutch coil spring 32, the clutch coil spring 32 transmits torque to the load torsion spring 33 through the connecting ring 31, and the load torsion spring 33 transmits torque to the shaft core 2 through the spring seat 4; the second transmission path is that torque can be directly transmitted from the pulley 1 to the load torsion spring 33, after which the load torsion spring 33 transmits torque to the spindle 2 through the spring seat 4. As shown in an AB section curve in fig. 10, the load torsion spring 33 receives the torque of the clutch coil spring 32, the axial length of the load torsion spring 33 abutting against the second annular cavity 12 gradually increases with the increase of the torque, at this time, a part of the outer side wall of the load torsion spring 33 abuts against the second annular cavity 12, the load torsion spring 33 does not have a vibration damping effect on the part abutting against the second annular cavity 12, and the load torque of the clutch coil spring 32 is always maintained at the point a; after the load torsion spring 33 is fully abutted against the inner wall of the second annular cavity 12, the curve at this time is at BC, the load torsion spring 33 is fully used for transmitting torque, and the load torque of the clutch coil spring 32 is always maintained at the point a.
The invention has the beneficial effects that: (1) The engine causes acceleration of the pulley 1 at the time of acceleration or at the time of high load of the generator, so that the torque increases. Firstly, the inner side wall of the belt pulley 1 is contacted with the clutch coil spring 32 to transmit low torque, and the torque is transmitted through the load torsion spring 33 along with the gradual increase of the torque, so that the torque can be transmitted from low to high, the sudden contact with the inner side wall of the belt pulley 1 under the condition of large torque of the load torsion spring 33 can be reduced, the load torsion spring 33 and the inner wall of the belt pulley 1 are greatly worn, and the service life of the load torsion spring 33 is shortened. That is, the torque transmission device can adapt to the transmission of torque in a larger range, so that the torque transmission device can be more stable, and noise and vibration can be effectively reduced.
(2) In the case of high load, there are two transmission paths compared to low load, so that a passage for mainly transmitting torque load is formed by the combination of the load torsion spring 33 and the inner side wall of the pulley 1 at high load, thereby protecting the clutch coil spring 32 and the load torsion spring 33.
(3) When the engine is decelerated, the deceleration of the belt pulley 1 is caused, and the generator and the shaft core 2 can continue to operate at a higher rotating speed by utilizing the unidirectional disengagement characteristic of the torsion spring.
(4) The pulley 1 is connected together through the clutch coil spring 32 and the load torsion spring 33, and the pulley 1 torque is transmitted to the axle core 2 through the clutch coil spring 32, the connecting ring 31 and the load torsion spring 33, and the torsional elasticity of the torsion spring is utilized to reduce the impact and vibration generated in the load transmission process.
Example 4: referring to fig. 4 and 9, an overrunning damper wheel with overload protection, comprising: the pulley 1, the axle core 2 and the torque transmission assembly 3, the torque transmission assembly 3 includes the go-between 31, clutch spring 32 and load torsional spring 33 all cover and establish in the axle core 2 outside, and go-between 31 can rotate around axle core 2 freedom, and the rigidity of load torsional spring 33 is greater than the rigidity of clutch spring 32.
The belt pulley 1 is internally provided with a belt pulley hole, the shaft core 2 is arranged in the belt pulley hole in a penetrating way, the belt pulley hole and the outer wall of the shaft core 2 are matched to form a first annular cavity 11 and a second annular cavity 12, the first annular cavity 11 and the second annular cavity 12 are communicated, the first annular cavity 11 and the second annular cavity 12 are coaxially arranged, the clutch coil spring 32 is arranged in the first annular cavity 11, and the load torsion spring 33 is arranged in the second annular cavity 12; the axial length of the second annular chamber 12 is greater than the axial length of the first annular chamber 11.
The first annular cavity 11 and the second annular cavity 12 in this embodiment are an integral annular cavity, a driving annular wall 13 is disposed in the radial direction in the integral annular cavity, the driving annular wall 13 is fixedly connected with the belt pulley 1, and the driving annular wall 13 and the belt pulley 1 are integrally formed in this embodiment. The end of the driving ring wall 13 is fixedly provided with an abutment ring 131, and in this embodiment the abutment ring 131 and the driving ring wall 13 are integrally formed. The inner diameter of the clutch coil spring 32 is in contact with the transmission annular wall 13 in an abutting mode, the end portion of the clutch coil spring 32 is in contact with the abutting ring 131 in an abutting mode, the connecting ring 31 is installed at the end portion of the integral annular cavity, and the abutting ring 131, the transmission annular wall 13 and the belt pulley 1 are integrally formed.
In this embodiment, two unidirectional ring seats are concentrically arranged on the connection ring 31, and the two unidirectional ring seats are respectively a unidirectional inner ring seat 311 and a unidirectional outer ring seat 312, the load torsion spring 33 is abutted against the unidirectional outer ring seat 312 of the connection ring 31, and the clutch coil spring 32 is abutted against the unidirectional inner ring seat 311 of the connection ring 31. Both the clutch coil spring 32 and the load torsion spring 33 have one end abutting the connection ring 31.
The load torsion spring 33 and the clutch coil spring 32 are rectangular in cross section, so that the contact area with the inner wall of the pulley 1 can be increased.
The end of the clutch coil spring 32 away from the connecting ring 31 abuts against the pulley 1, and the end of the clutch coil spring 32 abuts against the abutting ring 131 on the pulley 1, so that the rotation of the clutch coil spring 32 in the circumferential direction near the end of the pulley 1 can be restricted. The load torsion spring 33 is abutted against the spring seat 4 on the shaft core 2 at one end far away from the connecting ring 31, and the spring seat 4 in the embodiment is arranged on the outer side wall of the shaft core 2, and the spring seat 4 and the shaft core 2 are integrally formed. The spring seat 4 and the spindle 2 are integrally formed, and the spring seat 4 can restrict rotation of the end portion of the load torsion spring 33 in the circumferential direction.
The outer side wall of the end part of the shaft core 2 close to the shaft core is provided with an annular groove 22, a bushing 5 is arranged in the annular groove 22, and the outer side wall of the bushing 5 is abutted against the inner side wall of the belt wheel hole. The bushing 5 enables relative rotation between the shaft core 2 and the pulley 1. A bearing 6 is abutted between the outer side wall of one end of the shaft core 2 far away from the annular groove 22 and the inner side wall of the belt wheel hole. The function of the bearing 6 is similar to that of the bushing 5, allowing the free rotation of the shaft core 2 with respect to the pulley 1.
The end of the pulley bore adjacent the annular groove 22 is provided with a sealing cap 8. The sealing cover 8 can allow dust to enter the pulley hole while preventing the outflow of the internal grease.
The shaft core 2 is internally provided with a mounting hole 23, and the opening direction of the mounting hole 23 is opposite to that of the sealing cover 8. The mounting hole 23 is used for connecting with the rotating shaft of the generator.
The load torsion spring 33 may be provided in a shape having a large middle diameter and a small end diameter; the load torsion spring 33 may also be provided in a cylindrical shape of the same diameter; the second annular chamber 12 may be tapered or cylindrical. In the present embodiment, referring to fig. 7, the inside of the first and second annular chambers 11 and 12 is uniformly cylindrical, the clutch coil spring 32 is cylindrical, and the diameter of the load torsion spring 33 is gradually increased from one end toward the other end, so that the load torsion spring 33 forms a conical shape with an opening gradually increased. By providing the load torsion spring 33 in a tapered shape, the engagement length of the load torsion spring 33 and the inner wall of the pulley 1 is increased correspondingly with an increase in torque, so as to improve the adhesion ability; and the reduction of the work turns of the load torsion spring 33 causes the torsional rigidity of the load torsion spring 33 to continuously rise, so as to realize effective buffering under heavy load. The load torsion spring 33 may also be provided in a shape with a large middle diameter and a small end diameter; the load torsion spring 33 may also be provided in a cylindrical shape of the same diameter.
The installation process of this embodiment is as follows: one ends of both the clutch coil spring 32 and the load coil spring 33 are fitted with the connection ring 31 so that the torque of the clutch coil spring 32 can be transmitted to the load coil spring 33 through the connection ring 31. The other end of the load torsion spring 33 remote from the connecting ring 31 is placed on the spring seat 4 of the spindle 2, so that torque can be transmitted to the spindle 2 through the load torsion spring 33. The bushing 5 is installed in the annular groove 22 at the end of the shaft core 2, prevents the shaft core 2 from being in direct contact with the inner wall of the belt pulley 1, and plays a role in isolating and self-lubricating the bearing 6. The clutch coil spring 32 is expanded by a tool, the internal part is integrally placed into the pulley hole of the pulley 1, the clutch coil spring 32 is designed to be in interference fit with the first annular cavity 11 in a natural state, so that a tool hand is loosened, the inner diameter of the clutch coil spring 32 is contracted, and the clutch coil spring 32 and the inner wall of the first annular cavity 11 are combined together to transmit a certain torque load. Grease for lubrication is injected into the clutch coil spring 32, so that abrasion of the clutch coil spring 32 and the inner wall of the first annular cavity 11 is reduced, lubrication is increased when the load torsion spring 33 and the inner wall of the second annular cavity 12 are combined, and abrasion during separation and combination is reduced. And a bearing 6 is arranged to ensure that the belt pulley 1 and the shaft core 2 can rotate relatively, so that the installation of parts is completed. After the invention is installed on the generator, the sealing cover 8 is installed on the belt pulley 1 to prevent foreign matters from entering the inside of the belt pulley 1 and prevent the grease in the inside from flowing out.
The working principle in this embodiment is divided into two cases of high load and low load, and the two working conditions are discussed below, respectively.
(1) In a low load condition, the clutch coil spring 32 abuts against the side wall of the first annular cavity 11, the torque transmission path is that the belt pulley 1 transmits the torque to the clutch coil spring 32, the clutch coil spring 32 transmits the torque to the load torsion spring 33 through the connecting ring 31, and the load torsion spring 33 transmits the torque to the shaft core 2 through the spring seat 4. Because the torque at this time is small, the load torsion spring 33 is not greatly deformed, and thus the load torsion spring 33 does not transmit torque in contact with the inner side wall of the pulley 1. As shown in the OA section curve in fig. 10, the load torsion spring 33 at this time is not in contact with the inner side wall of the second annular chamber 12, and the torque of the pulley 1 is transmitted to the shaft core 2 through the clutch coil spring 32, the connecting ring 31 and the load torsion spring 33 in this order, and the load torsion spring 33 and the clutch coil spring 32 participate in vibration reduction at the same time.
(2) Under high load conditions, the clutch coil spring 32 accumulates enough torque to be transmitted to the load torsion spring 33 through the connecting ring 31, so that the load torsion spring 33 expands outwards, the load torsion spring 33 abuts against the side wall of the second annular cavity 12, so that the torque can be directly transmitted from the pulley 1 to the load torsion spring 33, and then the load torsion spring 33 transmits the torque to the shaft core 2 through the spring seat 4. That is, there are two transfer paths under high load. The first is the same as the transmission path of the low load, namely, the pulley 1 transmits to the clutch coil spring 32, the clutch coil spring 32 transmits torque to the load torsion spring 33 through the connecting ring 31, and the load torsion spring 33 transmits torque to the shaft core 2 through the spring seat 4; the second transmission path is that torque can be directly transmitted from the pulley 1 to the load torsion spring 33, after which the load torsion spring 33 transmits torque to the spindle 2 through the spring seat 4. As shown in an AB section curve in fig. 10, the load torsion spring 33 receives the torque of the clutch coil spring 32, the axial length of the load torsion spring 33 abutting against the second annular cavity 12 gradually increases with the increase of the torque, at this time, a part of the outer side wall of the load torsion spring 33 abuts against the second annular cavity 12, the load torsion spring 33 does not have a vibration damping effect on the part abutting against the second annular cavity 12, and the load torque of the clutch coil spring 32 is always maintained at the point a; after the load torsion spring 33 is fully abutted against the inner wall of the second annular cavity 12, the curve at this time is at BC, the load torsion spring 33 is fully used for transmitting torque, and the load torque of the clutch coil spring 32 is always maintained at the point a.
The invention has the beneficial effects that: (1) The engine causes acceleration of the pulley 1 at the time of acceleration or at the time of high load of the generator, so that the torque increases. Firstly, the inner side wall of the belt pulley 1 is contacted with the clutch coil spring 32 to transmit low torque, and the torque is transmitted through the load torsion spring 33 along with the gradual increase of the torque, so that the torque can be transmitted from low to high, the sudden contact with the inner side wall of the belt pulley 1 under the condition of large torque of the load torsion spring 33 can be reduced, the load torsion spring 33 and the inner wall of the belt pulley 1 are greatly worn, and the service life of the load torsion spring 33 is shortened. That is, the torque transmission device can adapt to the transmission of torque in a larger range, so that the torque transmission device can be more stable, and noise and vibration can be effectively reduced.
(2) In the case of high load, there are two transmission paths compared to low load, so that a passage for mainly transmitting torque load is formed by the combination of the load torsion spring 33 and the inner side wall of the pulley 1 at high load, thereby protecting the clutch coil spring 32 and the load torsion spring 33.
(3) When the engine is decelerated, the deceleration of the belt pulley 1 is caused, and the generator and the shaft core 2 can continue to operate at a higher rotating speed by utilizing the unidirectional disengagement characteristic of the torsion spring.
(4) The pulley 1 is connected together through the clutch coil spring 32 and the load torsion spring 33, and the pulley 1 torque is transmitted to the axle core 2 through the clutch coil spring 32, the connecting ring 31 and the load torsion spring 33, and the torsional elasticity of the torsion spring is utilized to reduce the impact and vibration generated in the load transmission process.
The above-described embodiments are merely preferred embodiments of the present invention, and the present invention is not limited in any way, and other variations and modifications may be made without departing from the technical aspects set forth in the claims.
Claims (10)
1. An overrunning shock absorbing wheel with overload protection, comprising: the belt pulley, the shaft core and the torque transmission assembly comprise a connecting ring, a clutch coil spring and a load torsion spring which are all sleeved on the outer side of the shaft core;
The belt pulley is provided with a belt pulley hole, the shaft core is arranged in the belt pulley hole in a penetrating way, the belt pulley hole and the outer wall of the shaft core are matched to form a first annular cavity and a second annular cavity, the first annular cavity is communicated with the second annular cavity, the clutch coil spring is arranged in the first annular cavity, and the load torsion spring is arranged in the second annular cavity;
One end of the clutch coil spring is abutted with the connecting ring, one end of the load torsion spring, which is far away from the connecting ring, is abutted with a spring seat on the shaft core, and one end of the clutch coil spring, which is far away from the connecting ring, is abutted with the belt pulley;
The clutch coil spring is always contacted with the radial direction of the first annular cavity, and the number of turns of the load torsion spring contacted with the second annular cavity changes along with the change of the transmitted torque;
The torque of the clutch coil spring energizes the load torsion spring so as to change the contact state of the load torsion spring and the second annular cavity; when the load torsion spring is in radial contact with the second annular cavity, part of torque of the belt pulley is directly transmitted to the shaft core through the load torsion spring, and the rest of torque of the belt pulley is sequentially transmitted to the shaft core through the clutch coil spring, the connecting ring and the load torsion spring.
2. The overrunning damping wheel with overload protection according to claim 1, wherein the connecting ring is concentrically provided with two unidirectional ring seats, and the clutch coil spring and the load torsion spring are respectively abutted against the two unidirectional ring seats.
3. The overrunning damper wheel with overload protection of claim 1 wherein the diameter of the load torsion spring increases progressively from one end to the other.
4. The overrunning damper wheel with overload protection of claim 1, wherein the diameter of the second annular chamber increases gradually from one end to the other.
5. The overrunning damper wheel with overload protection according to claim 1, wherein an end of the axle core is provided with an end cap, the spring seat is provided on the end cap, and the end of the load torsion spring away from the connecting ring abuts against the spring seat on the end cap.
6. The overrunning damper wheel with overload protection according to any one of claims 1 to 5 wherein the outer side wall of the end cap is provided with an annular groove, wherein a bushing is provided in the annular groove, the outer side wall of the bushing abutting the pulley aperture.
7. The overrunning damper wheel with overload protection of claim 6, wherein a bearing is abutted between an outer sidewall of an end of the axle core remote from the end cap and an inner sidewall of the pulley bore.
8. The overrunning damper wheel with overload protection according to claim 7, wherein the end face of the bearing adjacent to the end cap is provided with a spacer ring, and the connecting ring abuts against the spacer ring.
9. An overrunning damper wheel with overload protection according to any one of claims 1 to 5 wherein the end of the pulley aperture adjacent the end cap is provided with a sealing cap.
10. The overrunning damper wheel with overload protection according to claim 9, wherein the axle core is provided with a mounting hole, and the opening direction of the mounting hole is opposite to the sealing cover.
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| CN202410745800.XA CN118309779B (en) | 2024-06-11 | 2024-06-11 | Overrunning damping wheel with overload protection |
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| CN202410745800.XA CN118309779B (en) | 2024-06-11 | 2024-06-11 | Overrunning damping wheel with overload protection |
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| CN118309779B true CN118309779B (en) | 2024-09-06 |
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Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1890479A (en) * | 2003-12-09 | 2007-01-03 | 利滕斯汽车合伙公司 | Spring travel limitor for overrunning alternator decoupler |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| BRPI0312646B1 (en) * | 2002-07-26 | 2015-10-27 | Litens Automotive | decoupler assembly for transferring torque between a shaft and a drive belt; and, decoupler assembly for transferring torque between a motor driven crankshaft rod and a drive belt. |
| JP5507608B2 (en) * | 2005-10-31 | 2014-05-28 | 三ツ星ベルト株式会社 | Pulley structure |
| JP2007285369A (en) * | 2006-04-14 | 2007-11-01 | Ntn Corp | Spring clutch |
| US8678157B2 (en) * | 2011-05-25 | 2014-03-25 | Gates Corporation | Isolator decoupler |
| US9453538B2 (en) * | 2013-08-27 | 2016-09-27 | Litens Automotive Partnership | Isolator for engine with progressive lock-up for isolation spring |
| DE102015205612B3 (en) * | 2015-03-27 | 2015-12-17 | Schaeffler Technologies AG & Co. KG | Riemenscheibenentkoppler |
| US10087994B2 (en) * | 2016-04-19 | 2018-10-02 | Gates Corporation | Isolating decoupler |
| JP6747963B2 (en) * | 2016-12-21 | 2020-08-26 | 三ツ星ベルト株式会社 | Pulley structure |
| WO2023159324A1 (en) * | 2022-02-25 | 2023-08-31 | Litens Automotive Partnership | Decoupler with torque-limiting feature to protect components thereof |
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Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1890479A (en) * | 2003-12-09 | 2007-01-03 | 利滕斯汽车合伙公司 | Spring travel limitor for overrunning alternator decoupler |
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