Hydraulic multiplication centrifugal clutch

Abstract

The utility model relates to the technical field of clutches, in particular to a hydraulic multiplication 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, and hydraulic pistons extending out of the working cavities are embedded in the working cavities; hydraulic oil is filled between the flail block piston and the hydraulic piston in the pressure cavity and the working cavity, the pressure-bearing area of the flail block piston is smaller than that of the hydraulic piston, a dynamic friction disc is axially and slidably installed at the end, facing the driven shaft, of the mandrel, a static friction disc is coaxially arranged on the driven disc away from the dynamic friction disc, and 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. By means of the hydraulic multiplication effect, the hydraulic source moving mechanism and the hydraulic working mechanism are integrally designed, the size and the weight of a traditional centrifugal clutch are greatly reduced, and lightweight design is achieved.

Description

Technical Field

[0001] This utility model relates to the field of clutch technology, and in particular to a hydraulic multiplier centrifugal clutch. Background Technology

[0002] The clutch is installed between the engine and the transmission, and is an assembly in the drivetrain that is directly connected to the engine. Typically, the clutch is mounted together with the flywheel assembly of the engine crankshaft. The clutch can be operated as needed to temporarily separate or gradually engage the engine and drivetrain, cutting off or transmitting power from the engine to the drivetrain, thus achieving the disconnection and transmission of power between the engine and the drivetrain.

[0003] A centrifugal clutch transmits torque through friction. Its basic structure consists of three components: a driving element, a centrifugal body, and a driven element. The centrifugal body slides on the driving element and is driven by a prime mover to rotate and accelerate, thus throwing the centrifugal body radially out. When the driving element reaches a specified angular velocity, the thrown centrifugal body presses against the inner wall of the driven element, and the friction force forces it into motion to transmit torque.

[0004] Although the friction of a traditional centrifugal clutch varies with the centrifugal force, the friction generated by centrifugal pressure between the centrifugal component and the driven component is the same, which in turn makes the driving component of the driven component the same. In other words, the driving force of the driven component is entirely controlled by the rotational speed of the driving component, resulting in a single control method. Furthermore, to ensure power transmission or disconnection, existing centrifugal clutches have relatively complex structures and are too heavy overall.

[0005] Therefore, this utility model provides a hydraulic multiplier centrifugal clutch to achieve a lightweight design for centrifugal clutches. Utility Model Content

[0006] The purpose of this invention is to solve the problems existing in the prior art by proposing a hydraulic multiplier centrifugal clutch.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] A hydraulic multiplier centrifugal clutch includes a spindle connected to a power unit and a driven disc connected to a driven component. The spindle has a plurality of working chambers arranged in a ring on its end face facing the driven disc. The spindle sidewall has a pressure chamber arranged in a ring, communicating with the working chambers. A slinger piston is embedded in the pressure chamber. A hydraulic piston extending out of the working chamber is embedded in the working chamber. Hydraulic oil is filled between the slinger piston and the hydraulic piston in the pressure chamber and the working chamber. The pressure-bearing area of ​​the slinger piston is smaller than that of the hydraulic piston. A dynamic friction disc is axially slidably mounted on the spindle facing the driven shaft. A static friction disc is coaxially disposed on the driven disc away from the dynamic friction disc. The static friction disc is fixedly connected to the spindle. A spring is provided between the dynamic friction disc and the static friction disc.

[0009] Preferably, the driven disk has a diameter smaller than the diameters of the moving friction disk and the stationary friction disk. Both the moving and stationary friction disks have multiple through-holes arranged in a ring on their end faces. The spindle has threaded holes that correspond one-to-one with the limiting holes at the end facing the driven disk. Limiting screws are inserted into the corresponding limiting holes on the moving and stationary friction disks, and the limiting screws are threadedly connected to the corresponding threaded holes.

[0010] Preferably, both the dynamic friction disc and the spindle end face are provided with a plurality of corresponding pin holes, and guide pins are embedded in the pin holes of the dynamic friction disc and the spindle.

[0011] Preferably, the pressure chamber is located at the end of the piston away from the spindle axis, and an oil hole is provided between it and the working chamber.

[0012] Preferably, the pressure chamber is provided with a vent hole that penetrates the mandrel at the end of the piston facing the mandrel axis.

[0013] Preferably, the pressure chamber is open at one end away from the axis of the mandrel, and a sealing ring covering the pressure chamber is provided on the outer edge of the mandrel.

[0014] Preferably, both the moving friction disc and the stationary friction disc have multiple grooves arranged in a ring at their opposite ends, and the two ends of the spring are respectively embedded in the grooves of the moving friction disc and the stationary friction disc.

[0015] Preferably, the number of working chambers, pressure chambers, and oil holes satisfies the following conditions: the number of oil holes connecting each pressure chamber and the working chamber is the same, and the number of oil holes connecting each working chamber and the pressure chamber is the same.

[0016] Preferably, the moving friction disc, the stationary friction disc, the driven disc, and the spindle shaft are all provided with a central hole. An internal gear ring is provided on the inner wall of the central hole of the driven disc. The internal gear ring meshes with an external gear ring, and the external gear ring is connected to the driven component.

[0017] Preferably, both the central hole of the shaft and the central hole of the static friction disc are provided with bearings that cooperate with the driven component.

[0018] Compared with the prior art, this utility model provides a hydraulic multiplier centrifugal clutch, which has the following beneficial effects:

[0019] 1. This solution utilizes the centrifugal force generated by the rotation of the spindle driven by a power unit to drive the piston to squeeze the hydraulic oil in the pressure chamber and inject it into the working chamber. This squeezes the hydraulic piston, which in turn pushes the moving friction plate against the driven plate, achieving clutch disengagement and engagement. The hydraulic power source mechanism and the hydraulic working mechanism are integrated into a single design, significantly reducing the size and weight of traditional centrifugal clutches and achieving a lightweight design for centrifugal clutches.

[0020] 2. In this scheme, the pressure-bearing area of ​​the sling piston is smaller than that of the hydraulic piston. Based on Pascal's principle of isobaric fluid in a closed space, a hydraulic multiplication effect is achieved, which makes the driving force on the static friction disc exceed the centrifugal friction force of the traditional centrifugal clutch.

[0021] Other advantages, objectives and features of this invention will be set forth in part in the description which follows; and in part will be apparent to those skilled in the art upon examination of the following description; or may be taught from practice of this invention. Attached Figure Description

[0022] Figure 1 This is a right-view axial perspective three-dimensional schematic diagram of the present invention.

[0023] Figure 2 This is a left-facing axial perspective three-dimensional schematic diagram of the present invention.

[0024] Figure 3 For the present utility model Figure 1 A schematic diagram of the cross-section at point AA.

[0025] Figure 4 For the present utility model Figure 3 Schematic diagram of the cross-section at BB.

[0026] Figure 5 This is a schematic diagram of the cross-section of the working chamber and pressure chamber on the mandrel of this utility model at the oil hole.

[0027] Figure 6 For the present utility model Figure 3 A partial schematic diagram at point C.

[0028] Figure 7 For the present utility model Figure 3 An explosion diagram after the driven component has been removed.

[0029] Figure 8 This is a three-dimensional schematic diagram of the mandrel of this utility model.

[0030] Figure 9 This is a three-dimensional schematic diagram of the driven disk of this utility model.

[0031] Figure 10 For the present utility model Figure 3 A partial schematic diagram at point D.

[0032] Figure 11 For the present utility model Figure 1 An explosion diagram.

[0033] Figure 12 For the present utility model Figure 2 An explosion diagram.

[0034] In the diagram: 1. Sealing ring; 2. Mandrel; 3. Thrusting piston; 4. Bearing; 5. Hydraulic piston; 6. Guide pin; 7. Dynamic friction disc; 8. Driven disc; 9. Spring; 10. Static friction disc; 11. Limit screw; 12. Driven component; 13. Oil hole; 14. Vent hole; 15. Limit hole; 16. Threaded hole; 17. Pin hole; 18. Countersunk groove; 19. Internal gear ring; 20. External gear ring; 21. Working chamber; 22. Pressure chamber. Detailed Implementation

[0035] The following will refer to the appendix in the embodiments of this utility model. Figure 1-12 The technical solutions in the embodiments of this utility model will be clearly and completely described. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments.

[0036] Example 1: To address the problems existing in the prior art and achieve a lightweight design for centrifugal clutches, this example provides a hydraulic multiplier centrifugal clutch, including a spindle 2 connected to a power unit and a driven disc 8 connected to a driven component 12. The spindle 2 has a plurality of working chambers 21 arranged in a ring on its end face facing the driven disc 8. The sidewall of the spindle 2 has a pressure chamber 22 arranged in a ring, communicating with the working chambers 21. A slinger piston 3 is embedded in the pressure chamber 22. A hydraulic piston 5 extending out of the working chamber 21 is embedded in the working chamber 21. Hydraulic oil is filled between the slinger piston 3 and the hydraulic piston 5 in the pressure chamber 22 and the working chamber 21. The pressure-bearing area of ​​the slinger piston 3 is smaller than that of the hydraulic piston 5. A moving friction disc 7 is axially slidably mounted on the end of the spindle 2 facing the driven shaft. A stationary friction disc 10 is coaxially disposed on the driven disc 8 away from the moving friction disc 7. The stationary friction disc 10 is fixedly connected to the spindle 2. A spring 9 is provided between the moving friction disc 7 and the stationary friction disc 10.

[0037] Principle details of this embodiment:

[0038] A hydraulic multiplier centrifugal clutch includes a spindle 2 and a driven disc 8. The spindle 2 and the driven disc 8 are spaced apart along the same axis. The end of the spindle 2 opposite to the driven disc 8 is connected to a power unit, which inputs power; the driven disc 8 is connected to a driven member 12, and transmits power to the driven member 12.

[0039] The mandrel 2 has a plurality of hydraulic oil working chambers 21 arranged in a ring on the end face facing the driven disk 8, and a hydraulic piston 5 is embedded in each working chamber 21. The thickness of the hydraulic piston 5 is less than the depth of the working chamber 21, and the outer edge of the hydraulic piston 5 is sealed and fitted to the inner wall of the working chamber 21.

[0040] The outer edge of the mandrel 2 has a ring array of multiple hydraulic oil pressure chambers 22, and each pressure chamber 22 is embedded with a slinger piston 3. The thickness of the slinger piston 3 is less than the depth of the pressure chamber 22, and the outer edge of the slinger piston 3 is sealed and fitted to the inner wall of the pressure chamber 22.

[0041] The working chamber 21 is connected to the pressure chamber 22. The working chamber 21 is filled with hydraulic oil on the side of the hydraulic piston 5 facing the bottom wall of the working chamber 21, and the pressure chamber 22 is filled with hydraulic oil on the side of the throwing piston 3 away from the bottom wall of the working chamber 21. The hydraulic oil flows between the throwing piston 3 and the hydraulic piston 5 under pressure.

[0042] A moving friction disk 7 is axially slidably mounted on the end of the spindle 2 facing the driven disk 8, while a stationary friction disk 10 is provided on the side of the driven disk 8 away from the spindle 2. Multiple springs 9 are arranged in a ring array between the stationary friction disk 10 and the moving friction disk 7, and the stationary friction disk 10 moves synchronously with the moving friction disk 7 and the spindle 2. The spindle 2, the moving friction disk 7, the driven disk 8, and the stationary friction disk 10 are all coaxially arranged.

[0043] Based on the above technical solution:

[0044] When the power unit is stationary, the distance between the moving friction disc 7 and the stationary friction disc 10 is at its maximum under the elastic force of the spring 9. At this time, the moving friction disc 7 abuts against the hydraulic piston 5, causing the hydraulic piston 5 to move towards the bottom wall of the working chamber 21, thus separating the moving friction disc 7 from the driven disc 8. The clutch is in a power disengagement state and does not transmit power. At this time, the working chamber 21 shrinks, and hydraulic oil is squeezed into the pressure chamber 22. The hydraulic oil pressure in the pressure chamber 22 increases, thereby pushing the sling piston 3 to move towards the axis of the spindle 2.

[0045] When the power unit drives the spindle 2 to start rotating, the piston 3 installed in the spindle 2 is driven by centrifugal force to move away from the axis of the spindle 2, thereby squeezing hydraulic oil into the working chamber 21. The pressure in the hydraulic oil pressure chamber 22 increases, and the pressure in the hydraulic oil working chamber 21 increases accordingly. The hydraulic oil pressure acts on the hydraulic piston 5. However, when the spindle 2 rotates at a low speed, the hydraulic oil pressure cannot overcome the elastic force of the spring 9. At this time, although the moving friction disc 7 is under force, it will not move, and the clutch is still in a power disengaged state. As the rotational speed of the spindle 2 gradually increases, the centrifugal force of the piston 3 increases accordingly, and more hydraulic oil is squeezed into the working chamber 21. The hydraulic oil pressure gradually overcomes the elastic force of the spring 9, pushing the moving friction disc 7 closer to the driven disc 8 until the driven disc 8 is clamped between the moving friction disc 7 and the stationary friction disc 10. The moving friction disc 7 and the driven disc 8 are engaged, and the clutch is in the initial power engagement state. The driven disc 8 begins to output power to the driven component 12. As the rotational speed of the spindle 2 continues to increase, the centrifugal force of the piston 3 continues to increase, the hydraulic oil pressure continues to increase, and the engagement force between the moving friction disc 7 and the driven disc 8 increases. At this time, the clutch is in a power engagement state, and the driven disc 8 reliably outputs power to the driven component 12.

[0046] When the rotational speed of spindle 2 decreases, the above process reverses. That is, the centrifugal force on the piston 3 gradually decreases, and under the pressure of spring 9, the hydraulic oil flows back into pressure chamber 22, the moving friction disc 7 gradually disengages from the driven disc 8, and the power gradually separates.

[0047] In summary, this solution utilizes the centrifugal force generated by the rotation of the spindle 2 driven by the power unit to drive the piston 3 to squeeze the hydraulic oil in the pressure chamber 22 and inject it into the working chamber 21. This, in turn, squeezes the hydraulic piston 5, causing the moving friction disc 7 to engage with the driven disc 8, thus achieving clutch disengagement and engagement. The integrated design of the hydraulic power source mechanism and the hydraulic working mechanism significantly reduces the size and weight of traditional centrifugal clutches, achieving a lightweight design for centrifugal clutches.

[0048] In this design, the pressure-bearing area of ​​the slinger piston 3 is smaller than that of the hydraulic piston 5. Therefore, the diameter of the pressure chamber 22 is smaller than that of the working chamber 21, and the depth of the pressure chamber 22 is greater than that of the working chamber 21. At this time, the hydraulic power source mechanism (slinger piston 3) is a mechanism with a smaller pressure-bearing area and a longer stroke, while the hydraulic working mechanism (hydraulic piston 5) is a mechanism with a larger pressure-bearing area and a shorter stroke. Based on Pascal's principle of isobaric fluid in a closed space, a hydraulic multiplication effect is achieved.

[0049] In this design, the diameter of the driven disk 8 is smaller than that of the moving friction disk 7 and the stationary friction disk 10, so that the outer edge of the driven disk 8 is concealed within the moving friction disk 7. Both the moving friction disk 7 and the stationary friction disk 10 have multiple through-holes 15 arranged in a ring on their end faces, with the limit holes 15 located outside the outer edge of the driven disk 8. The mandrel 2 has threaded holes 16 corresponding to the limit holes 15 on one end facing the driven disk 8. Limit screws 11 are inserted into the corresponding limit holes 15 on both the moving friction disk 7 and the stationary friction disk 10, and are threadedly connected to the corresponding threaded holes 16. The moving friction disk 7 and the stationary friction disk 10 are connected in series by the limit screws 11, allowing both to slide axially relative to the mandrel 2. This achieves synchronous rotation between the moving friction disk 7, the stationary friction disk 10, and the mandrel 2, preventing speed differences between the moving friction disk 7 and the stationary friction disk 10 that would prevent the provision of stable power when clamping the driven disk 8. Preferably, the limiting screw 11 is a reducing screw, with the small diameter end being a threaded shaft that engages with the threaded hole 16; the large diameter end is a smooth shaft, the diameter of which is the same as the diameter of the limiting hole 15 on the moving friction disk 7 and the static friction disk 10, so as to avoid the threads interfering with the movement of the moving friction disk 7.

[0050] In this design, both the moving friction disk 7 and the spindle 2 have multiple corresponding pin holes 17 on their end faces, and guide pins 6 are embedded in the pin holes 17 of both the moving friction disk 7 and the spindle 2. The guide pins 6 further guide and restrict the axial movement of the moving friction disk 7 relative to the spindle 2, making the movement of the moving friction disk 7 more stable.

[0051] In this design, the pressure chamber 22 is located between the end of the piston 3 away from the axis of the spindle 2 and the working chamber 21, and is provided with an oil hole 13. The oil hole 13 enables communication between the pressure chamber 22 and the working chamber 21, thereby allowing hydraulic oil to flow between the pressure chamber 22 and the working chamber 21.

[0052] In this design, a vent hole 14 is provided in the pressure chamber 22 at the end of the piston 3 facing the axis of the spindle 2, penetrating the spindle 2. This vent hole is used to discharge air from the pressure chamber 22 on the side of the piston 3 facing the axis of the spindle 2, so as to prevent air resistance from occurring when the piston 3 is in centrifugal motion.

[0053] In this design, the pressure chamber 22 is open at one end opposite to the axis of the mandrel 2, and a sealing ring 1 is provided on the outer edge of the mandrel 2 to cover the pressure chamber 22. The pressure chamber 22 is open to prevent drilling on the mandrel 2 and the embedding of the piston 3; the sealing ring 1 seals the opening of the pressure chamber 22 to prevent hydraulic oil from leaking out. The sealing ring 1 is fastened to the mandrel 2 with screws.

[0054] In this design, both the moving friction disk 7 and the stationary friction disk 10 have multiple recessed grooves 18 arranged in a ring at their opposite ends. The two ends of the spring 9 are respectively embedded in the recessed grooves 18 of the moving friction disk 7 and the stationary friction disk 10. The recessed grooves 18 restrict the spring 9 to prevent it from shifting or even detaching. Alternatively, the spring 9 can be fitted onto a limiting screw 11, which also limits its movement and prevents it from shifting.

[0055] In this design, the number of working chambers 21, pressure chambers 22, and oil holes 13 satisfies the following conditions: the number of oil holes 13 connecting each pressure chamber 22 and working chamber 21 is the same, and the number of oil holes 13 connecting each working chamber 21 and pressure chamber 22 is the same. As shown in the attached diagram of this design, there are 3 pressure chambers 22 and 6 working chambers 21. Each pressure chamber 22 corresponds to 2 working chambers 21 and is provided with oil holes 13 to ensure that the oil pressure in each pressure chamber 22 and working chamber 21 is equal, thereby ensuring that the extrusion force exerted by the hydraulic piston 5 on the dynamic friction disc 7 is balanced.

[0056] In this design, the moving friction disc 7, the stationary friction disc 10, the driven disc 8, and the spindle 2 all have central holes. An internal gear ring 19 is provided on the inner wall of the central hole of the driven disc 8, meshing with an external gear ring 20, which is connected to the driven component 12. Through the meshing relationship between the internal gear ring 19 and the external gear ring 20, the driven disc 8 can drive the driven component 12 to rotate, thus achieving power transmission. The central holes not only provide space for the driven component 12 to be inserted and installed but also reduce the load on the components, thereby enhancing the lightweight design.

[0057] In this design, both the central hole of the spindle 2 and the central hole of the static friction disk 10 are equipped with bearings 4 that mate with the driven component 12. (See attached diagram.) Figure 3 As described above, after the outer gear ring 20 on the driven member 12 meshes with the inner gear ring 19, the shaft end of the driven member 12 penetrates into the central hole of the spindle 2, and through the two rows of bearings 4, additional mounting support is provided for the driven member 12, reducing the load pressure on the meshing surfaces of the inner gear ring 19 and the outer gear ring 20.

[0058] The above description is merely a preferred embodiment of this utility model, but the scope of protection of this utility model is not limited thereto. This patent introduces a design concept for a hydraulic multiplier centrifugal clutch. Clutch devices designed using this concept should all be within the scope of protection of this patent, including but not limited to: the number, material, and size of the sling pistons; the number, material, and size of the hydraulic pistons; and the type, number, and size of the springs. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in this utility model, based on the technical solution and inventive concept of this utility model, should be included within the scope of protection of this utility model.

[0059] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0060] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled 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 multiplier centrifugal clutch, characterized in that, The device includes a spindle (2) connected to a power unit and a driven disk (8) connected to a driven component (12). The spindle (2) has a plurality of working chambers (21) arranged in a ring on its end face facing the driven disk (8). The sidewall of the spindle (2) has a pressure chamber (22) arranged in a ring, communicating with the working chambers (21). A piston (3) is embedded in the pressure chamber (22). A hydraulic piston (5) extending out of the working chamber (21) is embedded in the working chamber (21). The pressure chamber (22) communicates with the working disk (12). Hydraulic oil is filled in the cavity (21) between the sling piston (3) and the hydraulic piston (5). The bearing area of ​​the sling piston (3) is smaller than that of the hydraulic piston (5). A dynamic friction disc (7) is axially slidably mounted on the end of the spindle (2) facing the driven shaft. A static friction disc (10) is coaxially arranged on the driven disc (8) away from the dynamic friction disc (7). The static friction disc (10) is fixedly connected to the spindle (2). A spring (9) is provided between the dynamic friction disc (7) and the static friction disc (10).

2. The hydraulic multiplier centrifugal clutch according to claim 1, characterized in that, The diameter of the driven disk (8) is smaller than that of the moving friction disk (7) and the stationary friction disk (10). Both the moving friction disk (7) and the stationary friction disk (10) have multiple through-holes (15) arranged in annular array on their end faces. The spindle (2) has threaded holes (16) that correspond one-to-one with the limit holes (15) on one end facing the driven disk (8). Limit screws (11) are inserted into the corresponding limit holes (15) on the moving friction disk (7) and the stationary friction disk (10). The limit screws (11) are threadedly connected to the corresponding threaded holes (16).

3. The hydraulic multiplier centrifugal clutch according to claim 1, characterized in that, The moving friction disk (7) and the spindle (2) are provided with a plurality of corresponding pin holes (17), and guide pins (6) are embedded in the pin holes (17) of the moving friction disk (7) and the spindle (2).

4. The hydraulic multiplier centrifugal clutch according to claim 1, characterized in that, The pressure chamber (22) is located at the end of the piston (3) away from the axis of the spindle (2), and an oil hole (13) is provided between it and the working chamber (21).

5. A hydraulic multiplier centrifugal clutch according to claim 1, characterized in that, The pressure chamber (22) is located at one end of the piston (3) facing the axis of the spindle (2) and has a vent hole (14) that passes through the spindle (2).

6. A hydraulic multiplier centrifugal clutch according to claim 1, characterized in that, The pressure chamber (22) is open at one end away from the axis of the spindle (2), and a sealing ring (1) covering the pressure chamber (22) is provided on the outer edge of the spindle (2).

7. A hydraulic multiplier centrifugal clutch according to claim 2, characterized in that, The moving friction disk (7) and the stationary friction disk (10) each have multiple grooves (18) arranged in a ring at one end opposite to each other. The two ends of the spring (9) are respectively embedded in the grooves (18) of the moving friction disk (7) and the stationary friction disk (10).

8. A hydraulic multiplier centrifugal clutch according to claim 4, characterized in that, The number of working chamber (21), pressure chamber (22) and oil holes (13) satisfies the following: the number of oil holes (13) connected to each pressure chamber (22) and working chamber (21) is the same, and the number of oil holes (13) connected to each working chamber (21) and pressure chamber (22) is the same.

9. A hydraulic multiplier centrifugal clutch according to claim 1, characterized in that, The moving friction disc (7), the stationary friction disc (10), the driven disc (8), and the spindle (2) are all provided with a central hole. An internal gear ring (19) is provided on the inner wall of the central hole of the driven disc (8). The internal gear ring (19) meshes with an external gear ring (20). The external gear ring (20) is connected to the driven component (12).

10. A hydraulic multiplier centrifugal clutch according to claim 9, characterized in that, The center hole of the spindle (2) and the center hole of the static friction disk (10) are both provided with bearings (4) that cooperate with the driven component (12).

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