A bidirectional torque transmission clutch with load release function

Abstract

The present invention aims to provide a bidirectional torque transmission clutch with a load-disengaging function, comprising a parallel-connected locking synchronous automatic clutch and a friction double-cone clutch. The locking synchronous automatic clutch comprises a locking and unlocking control cylinder, a sliding member locking outer tooth, a locking inner tooth, an input-end locking outer tooth, a drive tooth pair, and a helical tooth pair. The locking and unlocking control cylinder connects to and controls the movement of the inner teeth of the sliding member locking outer tooth, causing the sliding member locking outer tooth to engage, lock, or disengage with the input-end locking outer tooth. The locking and unlocking control cylinders are respectively connected to the drive tooth pair and the helical tooth pair and control their engagement. The present invention can disengage the clutch under input-end load conditions while also having the advantages of bidirectional torque transmission, high power density, and adaptability to high speeds.

Description

Technical Field

[0001] The present invention relates to a clutch, in particular to a two-way torque transmission clutch. Background Art

[0002] A bidirectional torque-transmitting clutch is one that, when engaged, can transmit torque from the input to the output and vice versa. Typical examples of bidirectional torque-transmitting clutches include various friction clutches and synchronized automatic clutches with an engagement lock. One-way overrunning clutches, such as friction roller clutches and conventional synchronized automatic clutches, are unable to transmit torque in the reverse direction. Friction clutches have the disadvantages of low power density, resulting in large size and weight. They also require a continuous supply of high-pressure hydraulic oil to transmit torque. This limitation, due to the sealing requirements of the high-pressure hydraulic oil and the dynamic balancing accuracy of the friction plates, makes friction clutches unsuitable for high-speed operation. Synchronized automatic clutches with an engagement lock can transmit torque in both directions, offering high power density and suitability for high-speed applications. However, compared to friction clutches, their disadvantage is that when transmitting torque in the reverse direction, if the input side becomes loaded, the synchronized automatic clutch cannot release the disengagement lock, resulting in a non-disengagement situation. Forced release of the disengagement lock can cause burrs and damage to the end faces of the locking teeth. Summary of the Invention

[0003] The object of the present invention is to provide a bidirectional torque transmission clutch with a load-disengaging function that can be disengaged under input-end load conditions.

[0004] The object of the present invention is achieved like this:

[0005] The present invention provides a bidirectional torque transmission clutch with a load disengagement function, which is characterized by comprising a parallel engagement locking synchronous automatic clutch and a friction double-cone clutch, wherein the engagement locking synchronous automatic clutch comprises a locking and unlocking control cylinder, a sliding member locking tooth outer tooth, a locking tooth inner tooth, an input end locking tooth outer tooth, a driving tooth pair, and a helical tooth pair, wherein the locking and unlocking control cylinder is connected to and controls the movement of the locking tooth inner tooth in the sliding member locking tooth outer tooth, so that the sliding member locking tooth outer tooth is engaged with the input end locking tooth outer tooth for locking or disengagement, and the locking and unlocking control cylinder is respectively connected to the driving tooth pair and the helical tooth pair and controls their socketing.

[0006] The present invention may also include:

[0007] 1. The outer teeth of the input end locking tooth are provided with an inclined surface, and the inner teeth of the locking tooth form an inclined surface angle α with the horizontal direction. The inclined surface angle α is smaller than the friction self-locking angle between the inner teeth of the locking tooth and the outer teeth of the input end locking tooth.

[0008] 2. The two sides of the two-way torque transmission clutch body are respectively connected to the fan and the motor / generator, and the fan is connected to the steam turbine through a common clutch; when power flows from the motor / generator, the helical gear pair is used to drive the gear pair to engage, and the engagement and locking synchronous automatic clutch is automatically engaged. Under the control of the lock and unlock control cylinder, the inner teeth of the locking gear move to the right, and the outer teeth of the locking gear at the input end are engaged with the outer teeth of the locking gear of the sliding part, completing the engagement and locking action. The inner teeth of the locking gear and the inclined surfaces of the outer teeth of the locking gear at the input end are not pressed tightly, and the torque is transmitted through the driving gear pair and the helical gear pair.

[0009] 3. The two sides of the two-way torque transmission clutch body are respectively connected to the fan and the motor / generator, and the fan is connected to the steam turbine through an ordinary clutch; when power flows from the steam turbine, the engagement lock synchronous automatic clutch cannot be disengaged due to the action of the engagement lock, and the α inclined surface of the inner teeth of the locking tooth is pressed against the inclined surface of the locking tooth at the input end. Under the action of the positive pressure of the inclined surface, the inner teeth of the locking tooth and the outer teeth of the locking tooth at the input end do not produce axial movement, and the torque is transmitted through the driving gear pair, the outer teeth of the locking tooth of the sliding part, the inner teeth of the locking tooth and the outer teeth of the locking tooth at the input end.

[0010] 4. The two sides of the two-way torque transmission clutch body are respectively connected to the fan and the motor / generator, and the fan is connected to the steam turbine through an ordinary clutch; when the load is disengaged, the friction double-cone clutch in parallel with the engaged lock synchronous automatic clutch engages, and power flows from the steam turbine. The torque is not transmitted through the engaged lock synchronous automatic clutch, and the motor / generator is in a follow-up state. The tooth surface clamping force between the inner teeth of the locking teeth and the outer teeth of the locking teeth at the input end is reduced or disappears. The lock unlocking control cylinder pushes the inner teeth of the locking teeth to move, unlocking the locked state. After the friction double-cone clutch is disengaged, the engaged lock synchronous automatic clutch automatically disengages to complete the load disengagement.

[0011] The advantages of the present invention are that the present invention can disengage the clutch under input-end load conditions, and has the advantages of bidirectional torque transmission, high power density, and adaptability to high speeds. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] Figure 1 The schematic diagram of the layout of a conventional steam-electric dual-drive unit (power flow when the steam turbine drives the load and generates electricity);

[0013] Figure 2 The schematic diagram of the layout of a conventional steam-electric dual-drive unit (power flow when the motor drives the load);

[0014] Figure 3 This is the layout principle diagram of the steam-electric dual-drive unit of the present invention (power flow when the motor drives the load);

[0015] Figure 4This is a schematic diagram of the layout of the steam-electric dual-drive unit of the present invention (power flow when the steam turbine drives the load, and the bidirectional torque transmission clutch of the present invention is in the engaged and locked state for reverse torque transmission);

[0016] Figure 5 The schematic diagram of the steam-electric dual-drive unit of the present invention (power flow when the steam turbine drives the load, and the two-way torque transmission clutch of the present invention is in the unlocked and disengaged state);

[0017] Figure 6 It is a structural schematic diagram of the present invention;

[0018] Figure 7 A schematic diagram of the structure in which the inner teeth of the locking teeth are disengaged from the outer teeth of the locking teeth at the input end;

[0019] Figure 8 It is a schematic diagram of the structure of the joint of the present invention;

[0020] Figure 9 A schematic diagram of the structure in which the inner teeth of the locking teeth engage with the outer teeth of the input end locking teeth;

[0021] Figure 10 This is a schematic diagram of the structure of the present invention that cannot be disengaged under the action of engagement and locking;

[0022] Figure 11 Schematic diagram of the forces acting on the inner teeth of the locking gear and the outer teeth of the locking gear at the input end when the load is released;

[0023] Figure 12 Schematic diagram of the engagement of the friction double cone clutch;

[0024] Figure 13 This is a schematic diagram of the inner teeth of the locking gear before they are disengaged from the outer teeth of the locking gear at the input end;

[0025] Figure 14 Schematic diagram of the inner teeth of the locking gear disengaging from the outer teeth of the input end locking gear;

[0026] Figure 15 This is a schematic diagram when the load is released. DETAILED DESCRIPTION

[0027] The present invention will be described in more detail below with reference to the accompanying drawings:

[0028] Combine Figure 1-15 The existing layout diagram of the steam-electric dual-drive unit is as follows: Figure 1 As shown, the steam turbine 5000, the conventional synchronous automatic clutch 4000, the motor / generator 2000, and the fan 3000 are connected in sequence.

[0029] like Figure 2As shown, when the conventional synchronous automatic clutch 4000 is in the disengaged state, the motor / generator 2000 is in the motor working state, which can directly drive the fan 3000 to operate, and the power flow 2100 is from 2000 to 3000.

[0030] like Figure 1 As shown, when the conventional synchronous automatic clutch 4000 is engaged, the steam turbine 5000 drives the fan 3000 and the motor / generator 2000, and the motor / generator 2000 switches to generator mode, with power flow 5100 flowing from 5000 to 3000. If a steam turbine failure occurs, the motor / generator 2000 switches to motor mode, driving the fan 3000. The steam turbine 5000 can be decelerated and shut down for maintenance. During this deceleration, the conventional synchronous automatic clutch 4000 automatically disengages. After maintenance is complete, the steam turbine 5000 speed is increased to the speed of the motor / generator 2000, and the conventional synchronous automatic clutch 4000 automatically engages, allowing the motor / generator 2000 to switch back to generator mode.

[0031] but Figure 1 The disadvantage of the steam-electric dual-drive unit shown is that once the motor / generator 2000 fails, the unit must be shut down for maintenance. The steam turbine 5000 and the motor / generator 2000 cannot serve as a backup for each other.

[0032] Figure 3 The steam-electric dual-drive unit shown includes a steam turbine 5000, a conventional synchronous automatic clutch 4000, a fan 3000, a clutch 1000 according to the present invention, and a motor / generator 2000, all connected in sequence. If either the motor / generator 2000 or the steam turbine 5000 fails, the faulty main engine can be slowed down for maintenance. After maintenance, the engine can be re-speeded to achieve dynamic paralleling.

[0033] Figure 3 In the embodiment, the power flow 2100 of the motor / generator 2000 driving the fan 3000 is 2000→1000→3000, the conventional synchronous automatic clutch 4000 is in a disengaged state, and the clutch 1000 of the present invention is in an engaged and locked state.

[0034] Figure 4 In the embodiment, the steam turbine 5000 drives the fan 3000 and the motor / generator 2000 in generator mode at the same time, and the power flow 5100 is 5000→4000→3000→1000→2000. At this time, the conventional synchronous automatic clutch 4000 is in the engaged state, and the clutch 1000 of the patented invention is in the engaged locked state of reverse torque transmission.

[0035] Figure 5In the embodiment, the steam turbine 5000 drives the fan 3000 to operate, the power flow 5200 is 5000→4000→3000, the conventional synchronous automatic clutch 4000 is in the engaged state, and the clutch 1000 of the patented invention is in the unlocked and disengaged state.

[0036] accomplish Figure 4 The power flow 5100 shown is Figure 5 The key to the power flow conversion shown is the clutch 1000 of the present invention. The clutch 1000 of the present invention should be able to transition from an engaged, locked state for reverse torque transmission to an unlocked, disengaged state. The clutch 1000 of the present invention should also be able to disconnect the load, meaning it can disengage when the output is loaded.

[0037] like Figure 6 As shown, the basic structure of the clutch 1000 of the present invention is a conventional engagement lockup clutch and a friction double cone clutch 1700 in parallel. Figure 7 It is a cross-sectional view of the sliding member locking tooth outer teeth 1500 , the locking tooth inner teeth 1400 and the input end locking tooth outer teeth 1300 .

[0038] The high-power disengaging locking synchronous automatic clutch and the low-power friction clutch 1700 are connected in parallel at the input end and the output end respectively.

[0039] The high-power disengaging locking synchronous automatic clutch transmits the main torque, and the low-power friction clutch 1700 does not transmit the main torque, but only assists the disengaging locking synchronous automatic clutch to disengage the locking teeth under the load condition at the input end (only a small counter-torque).

[0040] The working surfaces of the locking teeth of the output gear ring of the disengaged locking synchronous automatic clutch and the locking gear ring driven by the locking oil cylinder are repaired into inclined surfaces along the tooth width direction.

[0041] Before disconnecting the load, the friction clutch 1700 is engaged and bears the reverse torque. The locking gear ring moves under the drive of the locking cylinder, and a gap appears on the working surface of the locking tooth in the circumferential direction, and the locking tooth surface is no longer continuously pressed.

[0042] When the low-power friction clutch 1700 transmits reverse torque, the parts on the torque transmission route transmit torque in the circumferential direction without gaps. Its specific structure can be a friction double-cone clutch that uses a corrugated disk to connect the friction element and the input shaft, and a double-cone disk to output torque.

[0043] The high-power disengaging locking synchronous automatic clutch and the low-power friction clutch 1700 can be connected in sequence, arranged in an independent box and using the slip ring on the shaft section to provide the friction clutch working oil.

[0044] like Figure 8As shown, when the power flow 2100 is input, the helical gear pair 1200 drives the gear pair 1600 to engage, and the engagement lock synchronous automatic clutch in the clutch 1000 of the present invention is automatically engaged. Under the control of the lock unlocking control cylinder 1100, the locking gear inner teeth 1400 move to the right, and the input end locking gear outer teeth 1300 are engaged with the sliding member locking gear outer teeth 1500, completing the engagement lock action. However, the inclined surfaces of the locking gear inner teeth 1400 and the input end locking gear outer teeth 1300 are not pressed tightly, as shown in FIG. Figure 9 As shown. The torque is transmitted through the driving gear pair 1600 and the helical gear pair 1200. At this time, the clutch 1000 of the present invention is suitable for Figure 3 Working conditions shown.

[0045] like Figure 10 When the power flow direction is switched to 5100, the synchronous automatic clutch cannot be disengaged under the action of engagement lock, and the locking tooth inner tooth 1400 is pressed tightly against the input end locking tooth 1300. Figure 11 As shown, due to the specially designed inclined plane angle α being smaller than the friction self-locking angle, under the action of the positive pressure of the inclined plane, the locking tooth inner teeth 1400 and the input end locking tooth outer teeth 1300 will not produce axial movement. The torque can be transmitted through the driving gear pair 1600, the sliding member locking tooth outer teeth 1500, the locking tooth inner teeth 1400 and the input end locking tooth outer teeth 1300. At this time, the clutch 1000 of the present invention is suitable for Figure 4 Working conditions shown.

[0046] like Figure 10 、 Figure 11 As shown, when the load is to be released, it is difficult to directly control the locking and unlocking control cylinder 1100 to push the locking tooth inner teeth 1400 to move under the action of the positive pressure between the locking tooth inner teeth 1400 and the input end locking tooth outer teeth 1300. The thrust can be increased by increasing the cylinder diameter, but this method takes up a lot of space and is not the optimal solution. The solution adopted by the clutch 1000 of the present invention is to engage the friction double cone clutch 1700 connected in parallel with the conventional locking synchronous automatic clutch, and the power flow is as follows: Figure 12 As shown, the torque is no longer transmitted through the locked synchronous automatic clutch. At this time, the motor / generator 2000 is in a follow-up state and the load is very small, so only a small-power friction double-cone clutch 1700 is needed. Since the main torque has been borne by the friction double-cone clutch 1700, the tooth surface pressing force between the locking tooth inner teeth 1400 and the input end locking tooth outer teeth 1300 has been reduced or disappeared, and the locking and unlocking control cylinder 1100 can be controlled to push the locking tooth inner teeth 1400 to move, as shown in FIG. Figure 14 As shown, the locked state is unlocked, so that the clutch 1000 of the present invention is in Figure 15After the friction double cone clutch 1700 is disengaged, the locked synchronous automatic clutch will automatically disengage, completing the load disengagement function, that is, Figure 5 Working conditions shown.

Claims

1. A two-way torque transmission clutch with a load release function, characterized by: The invention comprises a parallel-connected locking synchronous automatic clutch and a friction double-cone clutch, wherein the locking synchronous automatic clutch comprises a locking and unlocking control oil cylinder, a sliding member locking tooth outer tooth, a locking tooth inner tooth, an input end locking tooth outer tooth, a driving tooth pair, and a helical tooth pair. The locking and unlocking control oil cylinder is connected to and controls the movement of the locking tooth inner tooth in the sliding member locking tooth outer tooth, so that the sliding member locking tooth outer tooth and the input end locking tooth outer tooth are engaged, locked, or disengaged. The locking and unlocking control oil cylinder is respectively connected to the driving tooth pair and the helical tooth pair and controls their sleeve connection. The outer teeth of the input end locking teeth are provided with an inclined surface, and the inner teeth of the locking teeth form an inclined surface angle α with the horizontal direction, and the inclined surface angle α is smaller than the friction self-locking angle between the inner teeth of the locking teeth and the outer teeth of the input end locking teeth; The two sides of the two-way torque transmission clutch body are respectively connected to the fan and the motor / generator. The fan is connected to the steam turbine via a conventional clutch. When power flows from the motor / generator, the helical gear pair engages the drive gear pair, causing the locking synchronous automatic clutch to automatically engage. Under the control of the locking and unlocking control cylinder, the inner teeth of the locking gear move to the right, engaging the outer teeth of the input-end locking gear with the outer teeth of the sliding member, completing the locking action. The inner teeth of the locking gear do not press against the inclined surfaces of the outer teeth of the input-end locking gear, and torque is transmitted through the drive gear pair and the helical gear pair. When power flows from the steam turbine, the engagement lock synchronous automatic clutch cannot be disengaged due to the action of engagement lock. The α inclined surface of the internal teeth of the locking tooth is pressed against the inclined surface of the input end locking tooth. Under the action of the positive pressure of the inclined surface, the internal teeth of the locking tooth and the external teeth of the input end locking tooth do not produce axial movement. The torque is transmitted through the driving gear pair, the external teeth of the sliding member locking tooth, the internal teeth of the locking tooth and the external teeth of the input end locking tooth. When the load is disengaged, the friction twin-cone clutch connected in parallel with the engaged lock-up synchronous automatic clutch engages, power flows into the steam turbine, torque is not transmitted through the engaged lock-up synchronous automatic clutch, the motor / generator is in a follow-up state, the tooth surface clamping force between the inner teeth of the locking teeth and the outer teeth of the locking teeth at the input end decreases or disappears, the lock-up unlocking control cylinder pushes the inner teeth of the locking teeth to move, unlocking the locked state. After the friction twin-cone clutch is disengaged, the engaged lock-up synchronous automatic clutch automatically disengages, completing the load disengagement.

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