Hydraulic self-locking centrifugal clutch

Abstract

The invention relates to the technical field of clutches, in particular to a hydraulic self-locking centrifugal clutch. Comprising a mandrel and a driven disc, a plurality of working cavities are annularly arrayed on the end face of the end, facing the driven disc, of the mandrel, pressure cavities communicated with the working cavities are annularly arrayed on the side wall of the mandrel, flail block pistons are embedded in the pressure cavities, hydraulic pistons are embedded in the working cavities, and a dynamic friction disc is axially installed at the end, facing the driven disc, of the mandrel in a sliding mode. The driven disc is coaxially provided with a static friction disc deviating from the dynamic friction disc, the static friction disc is fixedly connected with the mandrel, and a spring is arranged between the dynamic friction disc and the static friction disc; and a one-way rubber plug is arranged at the communicating part of the pressure cavity and the working cavity. According to the scheme, the hydraulic source moving mechanism and the hydraulic working mechanism are integrally designed, the size and weight of a traditional centrifugal clutch are greatly reduced, and lightweight design of equipment is achieved. And the flowing and cut-off of the hydraulic oil are controlled through the one-way rubber plug, so that the power self-locking of the clutch is realized, and the continuous output of the power is ensured.

Description

Technical Field

[0001] The present invention relates to the technical field of clutches, and in particular to a hydraulic self-locking centrifugal clutch. Background Art

[0002] The clutch is installed between the engine and the transmission, and is a component directly connected to the engine in the powertrain. Usually, the clutch is installed together with the flywheel group of the engine crankshaft. The clutch can be operated as needed to temporarily separate or gradually engage the engine and the powertrain, so as to cut off or transmit the power output from the engine to the powertrain, and realize the cut-off and transmission of power between the engine and the powertrain.

[0003] The centrifugal clutch transmits torque through friction. Its basic structure consists of three elements: the driving member, the centrifugal body and the driven member. The centrifugal body is slidably mounted on the driving member, and the driving member is driven by the prime mover to rotate and accelerate, and then the centrifugal body is radially thrown out. When the driving member reaches the specified angular velocity, the thrown centrifugal body presses against the inner wall of the driven member, and the driven member is forced into the motion state by friction to transmit torque.

[0004] Although the friction of the traditional centrifugal clutch changes with the change of the rotational centrifugal force, the friction generated by the centrifugal pressure between the centrifugal member and the driven member is the same, and then the driving member of the driven member is the same. That is to say, the driving force of the driven member is completely controlled by the rotational speed of the driving member, and the control method is single.

[0005] Therefore, the present invention will adopt the method of combining the hydraulic structure and the centrifugal mechanism to improve the power transmission of the centrifugal clutch, so that the binding force received by the driven member is increased. However, most general hydraulic structures squeeze the hydraulic oil through centrifugal force, and then squeeze the friction disc and the driven member to be combined to achieve power transmission. Although this makes the power output more stable and the combination more stable, when the power is transmitted by the combination of hydraulic pressure and centrifugal force, only when the rotational speed of the driving member reaches a certain level and the oil pressure of the hydraulic oil rises to a certain level, can the power transmission be realized, and there is an interval between starting and driving. As a result, the equipment cannot be applied to some scenarios where the power transmission control is relatively delicate. Such as power interruption and coupling devices of unmanned aerial vehicles and manned aircraft.

[0006] In addition, the overall volume of many devices combining centrifugal clutches and hydraulic superchargers will increase, which will limit the use scenarios of the devices.

[0007] For this reason, the present invention provides a hydraulic self-locking centrifugal clutch, which further modifies the centrifugal clutch and the hydraulic supercharging structure, so that the clutch can not only be combined / separated with the change of centrifugal force, but also realize hydraulic locking, that is, always combined; and realize lightweight design. Summary of the Invention

[0008] The object of the present invention is to solve the problems existing in the prior art, and a hydraulic self-locking centrifugal clutch is proposed.

[0009] To achieve the above object, the present invention adopts the following technical solutions: A hydraulic self-locking centrifugal clutch includes a core shaft connected to a power device and a driven disk connected to a driven member. A plurality of working chambers are annularly arrayed on the end face of one end of the core shaft facing the driven disk. Pressure chambers communicating with the working chambers are annularly arrayed on the side wall of the core shaft. Flyweight pistons are embedded in the pressure chambers, and hydraulic pistons are embedded in the working chambers. Hydraulic oil is filled between the flyweight pistons and the hydraulic pistons in the pressure chambers and the working chambers. A moving friction disk is axially slidably mounted at one end of the core shaft facing the driven shaft. A static friction disk is coaxially arranged on the driven disk away from the moving friction disk. The static friction disk is fixedly connected to the core shaft, and a spring is provided between the moving friction disk and the static friction disk. A one-way rubber plug is provided at the communicating part between the pressure chamber and the working chamber, and the one-way rubber plug can move to realize the conversion between the continuous penetration of the communicating part and the one-way penetration from the pressure chamber to the working chamber.

[0010] Preferably, a sealing ring is hermetically mounted on the outer wall of the core shaft at the position of the pressure chamber. An arc-shaped hydraulic oil path corresponding to each pressure chamber is provided on the inner wall of the sealing ring. An oil port communicating with the hydraulic oil path is provided at the port of one end of the pressure chamber away from the core shaft. The end of the hydraulic oil path is communicated with an oil hole communicating with the working chamber.

[0011] Preferably, self-locking threaded holes corresponding to the oil ports are provided on the outer wall of the sealing ring. Unlocking nuts are screwed in the self-locking threaded holes. The shaft end of the unlocking nut extends into the hydraulic oil path, and the one-way rubber plug is mounted on the shaft end of the unlocking nut.

[0012] Preferably, the one-way rubber plug is a conical plug, and a conical hole matching the conical plug is provided at the port of the oil port.

[0013] Preferably, the hydraulic oil path enables each pressure chamber to communicate with two opposite working chambers.

[0014] Preferably, a plurality of the hydraulic oil paths are axially spaced on the inner wall of the sealing ring, and the oil holes at both ends of the hydraulic oil path communicating with each other are symmetrically arranged.

[0015] Preferably, one end of the pressure chamber facing the sealing ring is open, and a cover is fixed at the opening. The oil port is provided on the cover.

[0016] Preferably, the diameter of the driven disk is smaller than that of the moving friction disk and the static friction disk. A plurality of through limiting holes are annularly arrayed on the end faces of the moving friction disk and the static friction disk. Limiting threaded holes corresponding to the limiting holes are provided at one end of the core shaft facing the driven disk. Limiting screws are commonly inserted into the corresponding limiting holes on the moving friction disk and the static friction disk, and the limiting screws are threadedly connected to the corresponding limiting threaded holes.

[0017] Preferably, a plurality of corresponding pin holes are provided on both the dynamic friction disc and the end face of the mandrel, and a guide pin is jointly embedded in the pin holes of the dynamic friction disc and the mandrel.

[0018] Preferably, an air vent hole penetrating the mandrel is provided on the side wall of the pressure chamber at one end of the flyweight piston facing the axis of the mandrel.

[0019] Compared with the prior art, the present invention provides a hydraulic self-locking centrifugal clutch, which has the following beneficial effects: 1. In this solution, the mandrel is driven to rotate by a power device, so that the flyweight piston generates centrifugal force, thereby squeezing the hydraulic oil to flow into the working chamber, driving the combination of the dynamic friction disc and the driven disc, and realizing the power output of the clutch. The entire hydraulic device is arranged on the mandrel, and the hydraulic oil is squeezed by the centrifugal force of the piston. The structure is simple, small in size and stable. The hydraulic power mechanism and the hydraulic working mechanism are integrally designed, greatly reducing the volume and weight of the traditional centrifugal clutch, and realizing the lightweight design of the equipment.

[0020] 2. As the centrifugal force gradually increases, the combination of the dynamic friction disc and the driven disc becomes tighter, and the power output becomes more stable.

[0021] 3. In this solution, a one-way rubber plug is arranged at the connecting part between the pressure chamber and the working chamber. By controlling the flow and cut-off of the hydraulic oil, the power self-locking of the clutch is realized, ensuring the continuous output of power, thus omitting the process of the combination of the dynamic friction disc and the driven disc, and improving the use flexibility of the equipment.

[0022] Other advantages, objectives and features of the present invention will be described to some extent in the subsequent description; and to some extent, based on the study of the following text, it will be obvious to those skilled in the art; or, it can be taught from the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a right-handed axial view three-dimensional schematic diagram of the present invention.

[0024] Figure 2 It is a left-handed axial view three-dimensional schematic diagram of the present invention.

[0025] Figure 3 It is for the present invention Figure 1 horizontal sectional schematic diagram.

[0026] Figure 4 It is for the present invention Figure 3 sectional schematic diagram at A-A.

[0027] Figure 5 It is for the present invention Figure 3 sectional schematic diagram at B-B.

[0028] Figure 6 Cross-sectional schematic diagram at C-C of the present invention Figure 3 .

[0029] Figure 7 Cross-sectional schematic diagram at D-D of the present invention Figure 3 .

[0030] Figure 8 Cross-sectional schematic diagram at E-E of the present invention Figure 4 .

[0031] Figure 9 Cross-sectional schematic diagram at G-G of the present invention Figure 8 .

[0032] Figure 10 Cross-sectional schematic diagram at F-F of the present invention Figure 7 .

[0033] Figure 11 Explosion schematic diagram of the present invention Figure 1 .

[0034] Figure 12 Explosion schematic diagram of the present invention Figure 2 .

[0035] Figure 13 Explosion schematic diagram after angle adjustment of the present invention

[0036] Figure 14 Three-dimensional schematic diagram of the mandrel in two directions of the present invention

[0037] Figure 15 Three-dimensional schematic diagram of the driven disk of the present invention

[0038] Figure 16 Three-dimensional schematic diagram of the driven member of the present invention Figure 17 Three-dimensional schematic diagram of the sealing ring of the present invention

[0039] Figure 18 Partial schematic diagram at H of the present invention Figure 4 .

[0040] Figure 19 Partial schematic diagram at J of the present invention Figure 9 .

[0041] Figure 20 Partial schematic diagram at K of the present invention Figure 18 .

[0042] Figure 21 Partial schematic diagram after opening of the one-way rubber plug of the present invention Figure 20 .

[0043] Figure 22 for the present invention Figure 6 Partial schematic view at position L

[0044] In the figure: 1, sealing ring; 2, mandrel; 3, flyweight piston; 4, unlocking nut; 5, one-way rubber plug; 6, driven member; 7, hydraulic piston; 8, guide pin; 9, driving friction disc; 10, driven disc; 11, spring; 12, static friction disc; 13, sunk groove; 14, limit screw; 15, hydraulic oil circuit; 16, oil hole; 17, oil port; 18, pressure chamber; 19, working chamber; 20, air vent hole; 21, limit hole; 22, limit threaded hole; 23, pin hole; 24, internal gear ring; 25, external gear ring; 26, cover. Specific embodiments

[0045] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying Figures 1-22 drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments.

[0046] Embodiment 1. To solve the problems existing in the prior art, this embodiment provides a hydraulic self-locking centrifugal clutch, which includes a mandrel 2 connected to a power device and a driven disc 10 connected to a driven member 6. On the end face of one end of the mandrel 2 facing the driven disc 10, a plurality of working chambers 19 are annularly arranged in an array. On the side wall of the mandrel 2, pressure chambers 18 communicating with the working chambers 19 are annularly arranged in an array. A flyweight piston 3 is embedded in the pressure chamber 18, and a hydraulic piston 7 is embedded in the working chamber 19. Hydraulic oil is filled between the flyweight piston 3 and the hydraulic piston 7 in the pressure chamber 18 and the working chamber 19. A driving friction disc 9 is axially slidably installed at one end of the mandrel 2 facing the driven shaft. A static friction disc 12 is coaxially arranged on the driven disc 10 facing away from the driving friction disc 9. The static friction disc 12 is fixedly connected to the mandrel 2, and a spring 11 is arranged between the driving friction disc 9 and the static friction disc 12; A one-way rubber plug 5 is arranged at the communicating part between the pressure chamber 18 and the working chamber 19, and the one-way rubber plug 5 can move to realize the conversion between the continuous penetration of the communicating part and the one-way penetration from the pressure chamber 18 to the working chamber 19.

[0047] Details of the principle of this solution: A hydraulic self-locking centrifugal clutch includes a mandrel 2 and a driven disc 10. The mandrel 2 and the driven disc 10 are arranged at intervals along the same axis. One end of the mandrel 2 facing away from the driven disc 10 is connected to a power device, and the power device inputs rotational power to the mandrel 2; the driven disc 10 is connected to a driven member 6 (generally the input shaft of components such as a gearbox), and the power is transmitted from the driven member to the driven member 6 to achieve power transmission.

[0048] The end surface of the core shaft 2 facing the driven disc 10 is provided with a plurality of hydraulic oil working chambers 19 in an annular array, and a hydraulic piston 7 is embedded in each working chamber 19. The thickness of the hydraulic piston 7 is less than the depth of the working chamber 19 to leave room for the movement of the hydraulic piston 7. The outer edge of the hydraulic piston 7 is sealed against the inner wall of the working chamber 19 to prevent leakage of the hydraulic oil.

[0049] There are multiple hydraulic oil pressure chambers 18 in a circular array on the outer edge surface of the core shaft 2, and a swing block piston 3 is embedded in each pressure chamber 18. The thickness of the swing block piston 3 is less than the depth of the pressure chamber 18 to leave room for the swing block piston 3 to move. The outer edge surface of the swing block piston 3 is sealed and fitted with the inner wall of the pressure chamber 18 to prevent hydraulic oil leakage. The pressure chamber 18 is located on the side of the working chamber 19 away from the driven disk 10 on the core shaft 2 to prevent trajectory interference between the pressure chamber 18 and the working chamber 19.

[0050] The working chamber 19 is connected to the pressure chamber 18, and the pressure chamber 18 and the working chamber 19 are filled with hydraulic oil between the swing block piston 3 and the hydraulic piston 7. A one-way rubber plug 5 is provided at the connecting portion between the pressure chamber 18 and the working chamber 19, and the one-way rubber plug 5 is movable to realize the conversion between the continuous penetration of the connecting portion and the one-way penetration from the pressure chamber 18 to the working chamber 19.

[0051] The core shaft 2 is provided with a dynamic friction disc 9 axially slidingly mounted on one end of the driven shaft, and the driven disc 10 is provided with a static friction disc 12 coaxially away from the dynamic friction disc 9, and the static friction disc 12 is fixedly connected to the core shaft 2, and a spring 11 is provided between the dynamic friction disc 9 and the static friction disc 12. Under the bidirectional extrusion of the spring 11 and the hydraulic oil, the hydraulic piston 7 always presses against the dynamic friction disc 9.

[0052] According to the above technical solution: When the power device is stationary, there is no centrifugal force, and the dynamic friction disc 9 tends to separate from the static friction disc 12 under the elastic force of the spring 11, and the dynamic friction disc 9, the static friction disc 12 and the driven disc 10 are not pressed together. At this time, the clutch is in a power separation state. Under the action of the spring 11, the dynamic friction disc 9 pushes the hydraulic piston 7 to move deeper into the working chamber 19. At this time, the hydraulic oil working chamber 19 shrinks, and the hydraulic oil is pressed back into the working chamber 19. The oil pressure in the hydraulic oil pressure chamber 18 increases, and the hydraulic oil pushes the swing block piston 3 to move toward the center of the core shaft 2.

[0053] When the power device drives the mandrel 2 to start rotating, the flyweight piston 3 installed in the pressure chamber 18 is driven by centrifugal force and tends to move away from the axis of the mandrel 2, thus squeezing the hydraulic oil in the pressure chamber 18 and squeezing it into the working chamber 19. The pressure in the hydraulic oil pressure chamber 18 increases, and the pressure in the hydraulic oil working chamber 19 increases accordingly. The hydraulic oil pressure acts on the hydraulic piston 7 and is transmitted to the driving friction plate 9 along the hydraulic piston 7. However, when the rotational speed of the mandrel 2 driven by the power device is relatively low, the centrifugal force on the flyweight piston 3 is small, so the moving distance of the flyweight piston 3 under pressure is small, the amount of hydraulic oil squeezed into the working chamber 19 is not high, and the oil pressure in the working chamber 19 does not rise much. At this time, the hydraulic oil pressure cannot overcome the elastic force of the spring 11, and the driving friction plate 9 and the driven plate 10 are still in a separated state, and the clutch is in a power-off state. When the rotational speed of the mandrel 2 gradually increases, the centrifugal force on the flyweight piston 3 increases accordingly, the amount of hydraulic oil squeezed into the working chamber 19 gradually increases, the oil pressure gradually increases, and the hydraulic oil pressure gradually overcomes the elastic force of the spring 11, and then pushes the driving friction plate 9 to approach and engage with the driven plate 10. At this time, the clutch is in a preliminary power engagement state, and the driven plate 10 starts to output power to the driven device. When the rotational speed of the mandrel 2 continues to increase, the centrifugal force on the flyweight piston 3 continues to increase, the hydraulic oil pressure increases accordingly, and the engagement force between the driving friction plate 9 and the driven plate 10 increases. At this time, the clutch is in a power engagement state, and the driven plate 10 reliably outputs power to the driven device.

[0054] When the rotational speed of the mandrel 2 driven by the power device decreases, the centrifugal force on the flyweight piston 3 decreases, and the hydraulic pressure is offset by the elastic force of the spring 11, causing the driving friction plate 9 to gradually tend to move away from the driven plate 10, realizing power cut-off.

[0055] In the self-locking working state, the driving one-way rubber plug 5 is moved to block the communicating part between the working chamber 19 and the pressure chamber 18, and the pressure chamber 18 and the working chamber 19 are no longer directly connected. When the oil pressure in the hydraulic oil pressure chamber 18 is greater than the oil pressure in the hydraulic oil working chamber 19, the hydraulic oil can flow from the working chamber 19 to the working chamber 19; when the oil pressure in the pressure chamber 18 is less than the oil pressure in the working chamber 19, the hydraulic oil cannot flow from the working chamber 19 to the pressure chamber 18. That is to say, at this time, the hydraulic oil flowing into the working chamber 19 stays here and does not overflow. Then the oil pressure of the hydraulic oil acts on the driving friction plate 9 through the hydraulic piston 7, and then drives the driving friction plate 9 to tightly press the driven plate 10 against the static friction plate 12, and the power can be continuously transmitted, thus realizing the power self-locking of the clutch and maintaining continuous power output. And at this time, even if the rotational speed of the mandrel 2 decreases, the hydraulic oil will not flow back into the pressure chamber 18 from the working chamber 19, and the above process is irreversible, and the power device and the driven device are always reliably connected.

[0056] Unlocking: When the power device stops operating, the centrifugal force on the flyweight piston 3 disappears, and the pressure in the hydraulic oil pressure chamber 18 drops to 0. At this time, the position of the one-way rubber plug 5 is adjusted, and the one-way rubber plug 5 no longer restricts the flow of hydraulic oil. Then, the spring 11 pushes the moving friction disk 9 towards the mandrel 2. The moving friction disk 9 pushes the hydraulic piston 7 to increase the pressure in the hydraulic oil working chamber 19. The hydraulic oil flows from the hydraulic oil circuit 15 to the hydraulic oil pressure chamber 18, and the moving friction disk 9 separates from the driven disk 10, achieving power cut-off.

[0057] In summary, in this solution, the power device drives the mandrel 2 to rotate, causing the flyweight piston 3 to generate centrifugal force, which squeezes the hydraulic oil into the working chamber 19, driving the combination of the moving friction disk 9 and the driven disk 10 to achieve the power output of the clutch. The entire hydraulic device is arranged on the mandrel 2, and the hydraulic oil is squeezed by the centrifugal force of the piston. The structure is simple, small in size and stable. The hydraulic power mechanism and the hydraulic working mechanism are integrated, greatly reducing the volume and weight of the traditional centrifugal clutch and realizing the lightweight design of the equipment. Moreover, as the centrifugal force gradually increases, the combination of the moving friction disk 9 and the driven disk 10 becomes tighter, and the power output becomes more stable. At the same time, by controlling the flow and cut-off of the hydraulic oil, the power self-locking of the clutch is realized, ensuring the continuous power output, thus eliminating the process of the combination of the moving friction disk 9 and the driven disk 10 and improving the flexibility of the equipment.

[0058] In this solution, the diameter of the driven disk 10 is smaller than that of the moving friction disk 9 and the static friction disk 12, so that the outer edge surface of the driven disk 10 is recessed into the moving friction disk 9. A plurality of through limiting holes 21 are annularly arranged on the end faces of the moving friction disk 9 and the static friction disk 12, and the limiting holes 21 are located outside the outer edge surface of the driven disk 10. One end of the mandrel 2 facing the driven disk 10 is provided with limiting threaded holes 22 corresponding to the limiting holes 21 one by one. Limiting screws 14 are inserted into the corresponding limiting holes 21 on the moving friction disk 9 and the static friction disk 12, and the limiting screws 14 are threadedly connected to the corresponding limiting threaded holes 22. The moving friction disk 9 and the static friction disk 12 are connected in series by the limiting screws 14, so that both the moving friction disk 9 and the static friction disk 12 are axially slidably engaged with the mandrel 2, thereby realizing the synchronous rotation between the moving friction disk 9, the static friction disk 12 and the mandrel 2, and avoiding the speed difference between the moving friction disk 9 and the static friction disk 12, so that stable power cannot be provided when clamping the driven disk 10. Preferably, the limiting screw 14 is a variable-diameter screw. The small-diameter end is a threaded shaft for threaded engagement with the threaded hole; the large-diameter end is a smooth shaft, and the diameter of the smooth shaft is the same as the diameter of the limiting hole 21 on the moving friction disk 9 and the static friction disk 12 to prevent the thread from interfering with the movement of the moving friction disk 9.

[0059] In this solution, a plurality of mutually corresponding pin holes 23 are provided on both the end faces of the dynamic friction disk 9 and the core shaft 2, and a guide pin 8 is jointly embedded in the pin holes 23 of the dynamic friction disk 9 and the core shaft 2. The axial movement of the dynamic friction disk 9 relative to the core shaft 2 is further guided and restricted by the guide pin 8, making the movement of the dynamic friction disk 9 more stable.

[0060] Embodiment 2, in a further embodiment of this solution, a sealing ring 1 is fixedly installed on the core shaft 2 by screws, and the sealing ring 1 is located on the outer wall at the pressure chamber 18. An arc-shaped hydraulic oil passage 15 corresponding to the pressure chamber 18 one by one is provided on the inner wall of the sealing ring 1, and the hydraulic oil passage 15 is in a non-spiral state. And at the port of each pressure chamber 18 facing away from the core shaft 2, an oil port 17 communicating with the hydraulic oil passage 15 is provided, so that the pressure chamber 18 communicates with the hydraulic oil passage 15. Both ends of the plurality of hydraulic oil passages 15 are connected with oil holes 16, and the other ends of the oil holes 16 communicate with the corresponding working chambers 19 to realize the flow of hydraulic oil between the pressure chamber 18 and the working chamber 19.

[0061] Self-locking threaded holes corresponding to the oil ports 17 one by one are provided on the outer wall of the sealing ring 1, an unlocking nut 4 is screwed in the self-locking threaded holes, and the shaft end of the unlocking nut 4 extends into the hydraulic oil passage 15 and a one-way rubber plug 5 is installed on the shaft end of the unlocking nut 4. By screwing the self-locking nut, the driving of the one-way rubber plug 5 can be realized, and then the switching between the continuous opening and the one-way opening of the oil port 17 can be controlled.

[0062] In this embodiment, the one-way rubber plug 5 is a tapered plug, and a tapered hole matching the tapered plug is provided at the port of the oil port 17. A limiting ring is provided in the self-locking threaded hole. When the self-locking nut is screwed until it abuts against the limiting ring, the tapered surface of the one-way rubber plug 5 abuts against the tapered hole of the oil port 17, and the one-way rubber plug 5 is slightly deformed to squeeze and seal the oil port 17. However, when the oil pressure in the pressure chamber 18 gradually rises, the hydraulic oil in the oil port 17 surges up and squeezes the one-way rubber plug 5, so that the tapered surface of the one-way rubber plug 5 is compressed and contracted to form a flow gap for the hydraulic oil, so that the hydraulic oil in the pressure chamber 18 can still flow into the working chamber 19. However, the hydraulic oil in the working chamber 19 enters the hydraulic oil passage 15 through the oil hole 16 and converges towards the direction of the oil port 17 along the hydraulic oil passage 15, but it abuts against the tapered horizontal end surface of the one-way rubber plug 5. Even if the one-way rubber plug 5 is deformed under pressure, it will closely adhere to the tapered hole of the oil port 17, thereby preventing the hydraulic oil in the working chamber 19 from surging back, and then realizing the retention of the hydraulic oil in the working chamber 19.

[0063] Embodiment 3. In a further embodiment of the present solution, the hydraulic oil circuit 15 enables each pressure chamber 18 to communicate with two opposing working chambers 19. As shown in the drawings of the present solution, there are 3 pressure chambers 18 and 6 working chambers 19. Each pressure chamber 18 corresponds to a hydraulic oil circuit 15, and each hydraulic oil circuit 15 has two corresponding oil holes 16, and each oil hole 16 corresponds to a working chamber 19. This avoids the problem of uneven pressure in the hydraulic oil working chamber 19 caused by inconsistent pressures in multiple hydraulic oil pressure chambers 18.

[0064] Moreover, the hydraulic oil circuits 15 corresponding to the 3 pressure chambers 18 are axially spaced on the inner wall of the sealing ring 1, so that the oil ports 17 corresponding to the pressure chambers 18 are staggered and located on three different axial planes. And the perimeter of the arc-shaped hydraulic oil circuit 15 satisfies: the two oil holes 16 of the same hydraulic oil circuit 15 are arranged in circular symmetry. Referring to the attached Figure 5 attachment Figure 6 attachment Figure 7 shown, the six oil holes 16 of the three hydraulic oil circuits 15 are staggered in pairs. Even if there are differences in the oil pressures in different pressure chambers 18, the hydraulic pistons 7 in the two working chambers 19 corresponding to the same pressure chamber 18 still act on the driving friction disk 9 symmetrically with the same oil pressure, so that the multiple pressures received on the driving friction disk 9 are symmetrically balanced in pairs, and further the combined pressure of the driving friction disk 9 on the driven disk 10 is symmetrically balanced.

[0065] Embodiment 4. In a further embodiment of the present solution, one end of the pressure chamber 18 facing the sealing ring 1 is open, and a cover 26 is fixedly installed at the opening by screws, and the oil port 17 is arranged on the cover 26. The open design of the pressure chamber 18 is more convenient for processing and production, and the cover 26 is provided for arranging the oil port 17 to cooperate with the one-way rubber plug 5.

[0066] Embodiment 5. In a further embodiment of the present solution, an air vent hole 20 penetrating the core shaft 2 is provided on the side wall of the pressure chamber 18 at one end of the centrifugal block piston 3 facing the axis of the core shaft 2. It is used to discharge the air on the side of the centrifugal block piston 3 facing the axis of the core shaft 2 in the pressure chamber 18, so as to avoid the phenomenon of air resistance when the centrifugal block piston 3 performs centrifugal motion.

[0067] In the present solution, the driving friction disk 9, the static friction disk 12, the driven disk 10, and the axis of the core shaft 2 are all provided with central holes. An internal gear ring 24 is provided on the inner wall of the central hole of the driven disk 10, and the internal gear ring 24 meshes with an external gear ring 25, and the external gear ring 25 is connected to the driven member 6. The driven disk 10 can drive the driven member 6 to rotate through the meshing relationship between the internal gear ring 24 and the external gear ring 25, realizing power transmission. The provided central holes can not only provide an insertion and installation space for the driven member 6, but also reduce the load of the components, thereby enhancing the lightweight design.

[0068] In this solution, bearings for mating with the driven member 6 are provided in the central holes of both the mandrel 2 and the static friction disc 12. After the external gear ring 25 on the driven member 6 meshes with the internal gear ring 24, the shaft end of the driven member 6 penetrates into the central hole of the mandrel 2, and through two rows of bearings, additional installation support is provided for the driven member 6 to reduce the load pressure on the meshing surface of the internal gear ring 24 and the external gear ring 25.

[0069] As described above, only the preferred specific embodiments of the present invention are provided, but the protection scope of the present invention is not limited thereto. This patent introduces the design concept of a hydraulic multiplication centrifugal clutch. Clutch devices designed using this concept should all fall within the protection scope of this patent, including but not limited to: the number, material, and size of the flyweight pistons 3, the number, material, and size of the hydraulic pistons 7, the type, number, and size of the springs 11, etc. Any person skilled in the art within the technical scope disclosed by the present invention, making equivalent substitutions or changes based on the technical solution and inventive concept of the present invention, should be covered by the protection scope of the present invention.

[0070] In the description of this specification, the description referring to terms such as "one embodiment", "some embodiments", "example", "specific example", or "some examples" means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, without contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0071] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A hydraulic self-locking centrifugal clutch, characterized in that: The invention comprises a core shaft (2) connected to a power device and a driven disc (10) connected to a driven member (6); a plurality of working chambers (19) are arranged in an annular array on the end surface of the core shaft (2) facing the driven disc (10); a pressure chamber (18) in an annular array on the side wall of the core shaft (2) communicating with the working chamber (19); a swing block piston (3) is embedded in the pressure chamber (18); a hydraulic piston (7) is embedded in the working chamber (19); hydraulic oil is filled between the swing block piston (3) and the hydraulic piston (7) in the pressure chamber (18) and the working chamber (19); a dynamic friction disc (9) is axially slidably mounted on the core shaft (2) facing the driven shaft; a static friction disc (12) is arranged coaxially with the driven disc (10) away from the dynamic friction disc (9); the static friction disc (12) is fixedly connected to the core shaft (2); and a spring (11) is arranged between the dynamic friction disc (9) and the static friction disc (12); A one-way rubber plug (5) is provided at the connection point between the pressure chamber (18) and the working chamber (19); the one-way rubber plug (5) is movable to achieve a switch between continuous penetration of the connection point and one-way penetration from the pressure chamber (18) to the working chamber (19).

2. A hydraulic self-locking centrifugal clutch according to claim 1, characterized in that: A sealing ring (1) is installed on the outer wall of the core shaft (2) at the pressure chamber (18), and an arc-shaped hydraulic oil circuit (15) corresponding to the pressure chamber (18) is provided on the inner wall of the sealing ring (1). An oil port (17) communicating with the hydraulic oil circuit (15) is provided at the end of the pressure chamber (18) away from the core shaft (2), and an oil hole (16) communicating with the working chamber (19) is connected to the end of the hydraulic oil circuit (15).

3. A hydraulic self-locking centrifugal clutch according to claim 2, characterized in that: The outer wall of the sealing ring (1) is provided with a self-locking threaded hole corresponding to the oil port (17) in a one-to-one manner, and an unlocking nut (4) is screwed into the inner thread of the self-locking threaded hole. The axial end of the unlocking nut (4) extends into the hydraulic oil circuit (15) and a one-way rubber plug (5) is installed on the axial end of the unlocking nut (4).

4. A hydraulic self-locking centrifugal clutch according to claim 3, characterized in that: The one-way rubber plug (5) is a tapered plug, and the oil port (17) is provided with a tapered hole that matches the tapered plug.

5. A hydraulic self-locking centrifugal clutch according to claim 2, characterized in that: The hydraulic oil circuit (15) enables each pressure chamber (18) to communicate with two opposing working chambers (19).

6. A hydraulic self-locking centrifugal clutch according to claim 5, characterized in that: The plurality of hydraulic oil circuits (15) are axially spaced apart on the inner wall of the sealing ring (1), and oil holes (16) communicating at both ends of the hydraulic oil circuits (15) are symmetrically arranged.

7. A hydraulic self-locking centrifugal clutch according to claim 4, characterized in that: The pressure chamber (18) is open at one end facing the sealing ring (1), and a sealing cover (26) is fixed at the opening. The oil port (17) is arranged on the sealing cover (26).

8. The hydraulic self-locking centrifugal clutch according to claim 1, characterized in that: The diameter of the driven disc (10) is smaller than that of the dynamic friction disc (9) and the static friction disc (12); the end surfaces of the dynamic friction disc (9) and the static friction disc (12) are provided with a plurality of through-going limiting holes (21) in an annular array; one end of the core shaft (2) facing the driven disc (10) is provided with limiting threaded holes (22) corresponding to the limiting holes (21) one by one; limiting screws (14) are inserted into the corresponding limiting holes (21) on the dynamic friction disc (9) and the static friction disc (12); the limiting screws (14) are threadedly connected to the corresponding limiting threaded holes (22).

9. The hydraulic self-locking centrifugal clutch according to claim 1, characterized in that: The end surfaces of the dynamic friction disc (9) and the core shaft (2) are both provided with a plurality of pin holes (23) corresponding to each other, and guide pins (8) are embedded in the pin holes (23) of the dynamic friction disc (9) and the core shaft (2).

10. The hydraulic self-locking centrifugal clutch according to claim 1, characterized in that: The pressure chamber (18) is provided with a vent hole (20) penetrating the core shaft (2) on the side wall of the swing block piston (3) at one end facing the axis of the core shaft (2).

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