Dual-power driving system using hydraulic automatic clutch device

Abstract

The utility model provides a dual-power driving system using a hydraulic automatic clutch device. The dual-power driving system is composed of a first power unit, a second power unit, the hydraulic clutch device and a control device. The first power unit and the second power unit are connected with the hydraulic clutch device through couplings, and the control device is electrically connected with the hydraulic device, the first power unit and the second power unit. The waste heat recovery device has the advantages that the problems that due to waste heat recovery in an intermittent fluctuation scene, equipment cannot run stably, and potential safety hazards exist are solved; 2, the equipment is reasonable in structure, convenient to use and high in efficiency; and 3, the problem that the service life of the circuit breaker is shortened or the potential safety hazard of electrical equipment is damaged due to frequent closing of an electrical control system can be solved.

Description

Technical Field

[0001] The utility model relates to a dual-power drive system, in particular to a dual-power drive system using a hydraulic automatic clutch device. Background Art

[0002] Dual-power drive systems are widely used in various industrial fields, and screw expanders are also one of them in industrial waste heat recovery. Screw expanders have been in the process of industrial waste heat recovery for some time. When the waste heat output is stable, the screw expander can drive the generator to generate electricity or drive other loads to operate stably and normally. However, when the waste heat output is unstable, especially in intermittent venting or fluctuations, if the conventional electrical control scheme similar to the stable waste heat output is continued, the circuit breaker will be frequently closed and opened, causing power grid shocks and threats to power grid safety and a sharp reduction in the service life of the circuit breaker. Therefore, for a long time, this type of waste heat has not been well utilized, resulting in a large amount of energy loss of high-quality steam and waste of water resources. How to solve the technical problem of screw expanders being able to recover this type of waste heat normally has become a difficult problem for technicians in this technical field for some time. Utility Model Content

[0003] The purpose of the utility model is to propose a dual-power drive system using a hydraulic automatic clutch device in response to the technical problems existing in the prior art in the application of dual-power drive systems in intermittent fluctuation scenarios, so that the screw expander can normally recover the waste heat whose output is unstable and in an intermittent fluctuation state, providing a technical solution for the recovery of such waste heat.

[0004] The purpose of the utility model can be achieved by the following technical scheme: a dual-power drive system using a hydraulic automatic clutch device, which includes a first power unit and a second power unit, and is characterized in that it also includes a hydraulic clutch device and a control device; the first power unit and the second power unit are respectively connected to the hydraulic clutch device through a coupling, and the control device is respectively electrically connected to the hydraulic device, the first power unit, and the second power unit. The hydraulic clutch device includes a transmission, a transmission main shaft, a rotary oil supply device, a sleeve, an axial oil supply seal, a piston cylinder sleeve, a speed difference sensor, a friction pair, a bearing, an outer ring transmission sleeve, a connecting shaft, a torque limiter, a protective cover, and a hydraulic station; the connection between them is: the rotary oil supply device is arranged in the center hole at the left end of the transmission main shaft, and oil is supplied through the axial hole. The sleeve is sleeved on the transmission main shaft, and an axial oil supply seal is arranged at the connection between them. The piston cylinder sleeve is spirally connected to the sleeve. The inner cavity of the piston cylinder sleeve is provided with a reset spring and a hydraulic piston. The speed difference sensor is arranged at the speed measurement position on the transmission. The shaft sleeve is provided with axial connecting teeth connected to the inner ring transmission friction pair. The bearing sleeve is mounted on the shaft platform at the end of the main shaft of the transmission. The outer peripheral wall of the bearing is connected to the inner hole of the gear coupling so that it functions as a bearing seat. The gear coupling and the outer ring transmission sleeve are connected by connecting bolts. The outer ring transmission sleeve is provided with axial connecting teeth connected to the outer ring transmission friction pair. The fixed baffle is fixed on the outer ring transmission sleeve. The bearing gland is fixed to the bearing by fastening bolts through the center hole of the reducer main shaft. The gear coupling and the outer ring transmission sleeve are connected by connecting bolts. One end of the protective cover is fixed to the transmission housing, and the other end is suspended on the connecting shaft. A shaft seal is installed on the protective cover. The gear coupling is connected to the torque limiter through the connecting shaft, and the torque limiter is connected to the generator or load. The hydraulic station is connected to the rotary oil supply device through a pipeline. The control device is mainly composed of a PLC, which processes the signal sent from the speed difference sensor 7 and issues instructions to other devices in the whole. The PLC model is SIMATIC S7-1500.

[0005] The beneficial effects of the utility model are as follows: 1. It utilizes the first power unit of the screw expander with excellent anti-fluctuation performance, and integrates a hydraulic automatic clutch device for dual-power drive with a reducer for design, and systematically transmits the torque provided by the first power unit and the second power unit to the generator or load through a hydraulic automatic clutch device for dual-power drive; the second power unit only serves to stabilize the speed of the generator or load, and the first power unit can provide a recovery solution for the efficient utilization of intermittent heat sources or seasonal waste heat. The first power unit is driven and operated with the energy recovered by the screw expander first, which eliminates the problem of equipment not being able to operate stably due to unstable or intermittent waste heat sources, and reduces the difficulty of recovery and the devastating safety hazards caused by frequent start-stop of waste heat recovery equipment;

[0006] 2. Since the friction pair has no relative motion during operation, the design can achieve frequent clutching for an extremely long time and is maintenance-free. Since a split external oil supply method is adopted, the hydraulic station and the dual-power-driven hydraulic automatic clutch device have a split structure, so when repairing the hydraulic station, there is no need to disassemble the reducer chassis, which is convenient, simple, time-saving and improves efficiency.

[0007] 3. The utility model can also solve the electrical safety hazard of reducing the life of or damaging the circuit breaker due to frequent closing of the electrical control system.

[0008] The utility model is further described below in conjunction with the accompanying drawings and embodiments: BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Attached Figure 1 This is a schematic diagram of the main structure of the utility model;

[0010] Attached Figure 2 It is a schematic diagram of the top view structure of the utility model;

[0011] Attached Figure 3 For attachment Figure 2 The enlarged schematic diagram of the axial cross-section structure at B-B in the middle;

[0012] Attached Figure 4 For attachment Figure 1 Enlarged schematic diagram of the transverse cross-section structure at AA in the middle;

[0013] Attached Figure 5 This is a schematic diagram of the block structure of Embodiment 1 of the present utility model;

[0014] Attached Figure 6 This is a schematic diagram of the block structure of Embodiment 2 of the present utility model;

[0015] Attached Figure 7 It is a schematic diagram of the control principle block structure of the automatic clutch device in the utility model. DETAILED DESCRIPTION

[0016] It should be noted that the embodiments listed below are only examples of the present technical solution. Other embodiments with the same functions as the present technical solution obtained by those skilled in the art without making any creative work shall all fall within the scope of protection of the present technical solution.

[0017] Example 1, see attached Figure 1 , 2, 3, 4, 5, 7, a dual-power drive system using a hydraulic automatic clutch device, which is mainly composed of a screw expander (first power unit, the same below) A, a generator (second power unit, the same below) B, a hydraulic clutch device C, a control device D, a laminated flexible coupling E, and a pin-type coupling G. The screw expander A and the hydraulic clutch device C are connected through the laminated flexible coupling E, the generator B and the hydraulic clutch device C are connected through the pin-type coupling G; the control device D is electrically connected to the hydraulic clutch device C, the screw expander A, and the generator B, respectively.

[0018] The hydraulic clutch device C is mainly composed of a transmission 1, a transmission main shaft 2, a rotary oil supply device 3, a sleeve 4, an axial oil supply seal 5, a piston cylinder sleeve 6, a speed difference sensor 7, an inner ring transmission friction pair 8, an outer ring transmission friction pair 9, a bearing 10, an outer ring transmission sleeve 11, a gear coupling 12, a torque limiter 13, a connecting shaft 14, a protective cover 15, a hydraulic station 16, a fixed baffle 17, a bearing gland 18, and a shaft seal 19. The connection between them is as follows: the rotary oil supply device 3 is arranged in the center hole at the left end of the transmission main shaft, and oil is supplied through the axial center hole. The sleeve 4 is sleeved on the transmission main shaft 2, and the outer part of the sleeve 4 is provided with an annular groove for the piston to run, and a return spring 41 is arranged in the annular groove. An axial oil supply seal 5 is arranged at the joint between the sleeve 4 and the transmission main shaft 2. The piston cylinder sleeve 6 is spirally connected to the sleeve 4. The inner cavity of the piston cylinder sleeve 6 is provided with a hydraulic piston 61. A part of the hydraulic piston 61 is in contact with the inner ring transmission friction pair 8, and the other part is in contact with one end of the return spring 41. The speed difference sensor 7 is arranged at the speed measuring position on the transmission 1. The bearing 10 is sleeved on the pillow block at the end of the transmission main shaft 2, and the outer peripheral wall of the bearing 10 is connected with the inner hole of the gear coupling 12 so that it functions as a bearing seat. The gear coupling 12 and the outer ring transmission sleeve 11 are connected by connecting bolts. The shaft sleeve 4 is provided with axial connecting teeth 42 connected to the inner ring transmission friction pair 8, and the outer ring transmission sleeve 11 is provided with axial connecting teeth 111 connected to the outer ring transmission friction pair 9. The fixed baffle 17 is fixed to the outer ring transmission sleeve 11. The bearing gland 18 fixes the bearing 10 by fastening bolts through the center hole of the transmission main shaft 2. The gear coupling 12 and the outer ring transmission sleeve 11 are connected by connecting bolts. One end of the protective cover 15 is fixed to the transmission 1 housing, and the other end is suspended on the connecting shaft 14. A shaft seal 19 is installed on the protective cover 15. The gear coupling 12 is connected to the torque limiter 13 through the connecting shaft 14, and the torque limiter 13 is connected to the generator or the load. The hydraulic station 16 is connected to the rotary oil supply device 3 through a pipeline. The control device is mainly composed of a PLC, which processes the signal sent from the speed difference sensor 7 and issues instructions to other devices in the whole. The PLC model is SIMATIC S7-1500.

[0019] The operation process of the device is as follows: when the hydraulic clutch device C is engaged, the hydraulic piston 61 generates axial movement under the action of oil pressure, compressing the reset spring 41 to store force, and at the same time compressing the inner ring transmission friction pair 8 and the outer ring transmission friction pair 9 to also generate axial movement. Due to the obstruction of the fixed baffle 17, the inner ring transmission friction pair 8 and the outer ring transmission friction pair 9 are tightly attached, and the friction force is the largest at this time, so that the torque of the screw expander A is transmitted to the generator B; when the hydraulic clutch device C is disengaged, the pressure relief valve of the hydraulic station 16 is quickly opened, and the hydraulic piston 61 is quickly depressurized. Under the action of the reset spring 41, an axial reset movement is generated, and the inner ring transmission friction pair 8 and the outer ring transmission friction pair 9 are separated. At this time, the friction force is the smallest, a speed difference is generated, and the bearing 10 rotates, so that the screw expander A is completely separated from the generator B; considering that under extreme conditions, when the hydraulic system fails, if the clutch cannot be disengaged, the screw expander A will become a load. At this time, since the torque will exceed the protection value of the torque limiter 13, it will automatically disconnect from the generator B, so as to achieve the purpose of protecting the equipment in the shaft system.

[0020] The control process of this device is: first, it is necessary to set the parameter values ​​of screw expander A (such as the pressure and synchronous speed value of waste heat steam) and the starting parameters of generator B (such as speed). The control system will determine whether screw expander A meets the starting conditions based on the set parameters. If the starting conditions are met, the system will automatically start screw expander A to run at the set operating speed; during operation, the system will always detect the speed difference between generator B and screw expander A. After the conditions are met, the system will automatically open the oil supply valve to make the hydraulic clutch device engage and work; when it is determined that screw expander A does not meet the starting conditions, screw expander A will enter idle operation and repeatedly detect the speed difference between the dual powers and the status of the waste heat setting parameters, waiting for the next engagement signal; when a speed difference occurs between the two speeds or the waste heat parameter is lower than the set value, the system will automatically close the oil supply valve and open the oil unloading valve at the same time to achieve switching or shutdown between powers.

[0021] Example 2, see attached Figure 1 , 2, 3, 4, 6, 7, a dual-power drive system using a hydraulic automatic clutch device, which is mainly composed of a screw expander (first power unit, the same below) A, a generator B, a hydraulic clutch device C, a control device D, a laminated flexible coupling E, a pin-type coupling G, and a turbine (second power unit, the same below) F. The screw expander A and the hydraulic clutch device C are connected through the laminated flexible coupling E, the hydraulic clutch device C and the generator B are connected through the pin-type coupling G, and the generator B and the turbine F are connected through the laminated flexible coupling E (Note: the generator B, as a passive power generation device, belongs to the load). The torque generated by the two power units is jointly transmitted to the generator to generate electrical energy. The control device D is electrically connected to the hydraulic clutch device C, the screw expander A, the generator B, and the turbine F respectively (Note: the second power unit can be of various types, which can be a turbine, a generator, or a steam turbine, etc.).

[0022] The hydraulic clutch device C is mainly composed of a transmission 1, a transmission main shaft 2, a rotary oil supply device 3, a sleeve 4, an axial oil supply seal 5, a piston cylinder sleeve 6, a speed difference sensor 7, an inner ring transmission friction pair 8, an outer ring transmission friction pair 9, a bearing 10, an outer ring transmission sleeve 11, a gear coupling 12, a torque limiter 13, a connecting shaft 14, a protective cover 15, a hydraulic station 16, a fixed baffle 17, and a bearing gland 18. The connection between them is: the rotary oil supply device 3 is arranged in the center hole at the left end of the transmission main shaft, and oil is supplied through the axial hole. The sleeve 4 is sleeved on the transmission main shaft 2, and an axial oil supply seal 5 is arranged at the connection between them. The piston cylinder sleeve 6 is spirally connected to the sleeve 4. The inner cavity of the piston cylinder sleeve 6 is provided with a reset spring 61 and a hydraulic piston 62. The speed difference sensor 7 is arranged at the speed measurement position on the transmission 1. The bearing 10 is sleeved on the pillow block at the end of the transmission main shaft 2, and the outer peripheral wall of the bearing 10 is connected with the inner hole of the gear coupling 12 so that it functions as a bearing seat. The gear coupling 12 and the outer ring transmission sleeve 11 are connected by connecting bolts. The shaft sleeve 4 is provided with axial connecting teeth 42 connected to the inner ring transmission friction pair 8, and the outer ring transmission sleeve 11 is provided with axial connecting teeth 111 connected to the outer ring transmission friction pair 9. The fixed baffle 17 is fixed on the outer ring transmission sleeve 11. The bearing gland 18 fixes the bearing 10 by fastening bolts through the center hole of the transmission main shaft 2. The gear coupling E1 and the outer ring transmission sleeve 11 are connected by connecting bolts. One end of the protective cover 15 is fixed on the transmission 1 housing, and the other end is suspended on the connecting shaft 14. A shaft seal is installed on the protective cover 15. The gear coupling 12 is connected to the torque limiter 13 through the connecting shaft 14, and the torque limiter 13 is connected to the generator or the load. The hydraulic station 16 is connected to the rotary oil supply device 3 through a pipeline. The control device is mainly composed of a PLC, which processes the signal sent from the speed difference sensor 7 and issues instructions to other devices in the whole. The PLC model is SIMATIC S7-1500.

[0023] The operation process of the device is as follows: when the hydraulic clutch device C is engaged, the hydraulic piston 61 generates axial movement under the action of oil pressure, compressing the reset spring 41 to store force, and at the same time compressing the inner ring transmission friction pair 8 and the outer ring transmission friction pair 9 to also generate axial movement. Due to the obstruction of the fixed baffle 17, the inner ring transmission friction pair 8 and the outer ring transmission friction pair 9 are tightly attached, and the friction force is the largest at this time, so that the torque of the screw expander A is transmitted to the generator B; when the hydraulic clutch device C is disengaged, the pressure relief valve of the hydraulic station 16 is quickly opened, and the hydraulic piston 61 is quickly depressurized. Under the action of the reset spring 41, an axial reset movement is generated, and the inner ring transmission friction pair 8 and the outer ring transmission friction pair 9 are separated. At this time, the friction force is the smallest, a speed difference is generated, and the bearing 10 rotates, so that the screw expander A is completely separated from the generator B; considering that under extreme conditions, when the hydraulic system fails, if the clutch cannot be disengaged, the screw expander A will become a load. At this time, since the torque will exceed the protection value of the torque limiter 13, it will automatically disconnect from the generator B, so as to achieve the purpose of protecting the equipment in the shaft system.

[0024] The control process of this device is: first, it is necessary to set the parameter values ​​of screw expander A (such as the pressure and synchronous speed value of waste heat steam) and the starting parameters of generator B (such as speed). The control system will determine whether screw expander A meets the starting conditions based on the set parameters. If the starting conditions are met, the system will automatically start screw expander A to run at the set operating speed; during operation, the system will always detect the speed difference between generator B and screw expander A. After the conditions are met, the system will automatically open the oil supply valve to make the hydraulic clutch device engage and work; when it is determined that screw expander A does not meet the starting conditions, screw expander A will enter idle operation and repeatedly detect the speed difference between the dual powers and the status of the waste heat setting parameters, waiting for the next engagement signal; when a speed difference occurs between the two speeds or the waste heat parameter is lower than the set value, the system will automatically close the oil supply valve and open the oil unloading valve at the same time to achieve switching or shutdown between powers.

Claims

1. A dual-power drive system using a hydraulic automatic clutch device, comprising a first power unit and a second power unit, characterized in that It also includes a hydraulic clutch device and a control device; the first power unit and the second power unit are respectively connected to the hydraulic clutch device through a coupling, and the control device is respectively electrically connected to the hydraulic device, the first power unit and the second power unit.

2. A dual-power drive system using a hydraulic automatic clutch device according to claim 1, characterized in that: The hydraulic clutch device includes a transmission, a transmission main shaft, a rotary oil supply device, a sleeve, an axial oil supply seal, a piston cylinder sleeve, a speed difference sensor, a friction pair, a bearing, an outer ring transmission sleeve, a connecting shaft, a torque limiter, a protective cover, and a hydraulic station; the connection between them is as follows: the rotary oil supply device is arranged in the center hole at the left end of the transmission main shaft, and oil is supplied through the axial hole; the sleeve is sleeved on the transmission main shaft, and an axial oil supply seal is arranged at the connection between them; the piston cylinder sleeve is spirally connected to the sleeve; the inner cavity of the piston cylinder sleeve is provided with a reset spring and a hydraulic piston; the speed difference sensor is arranged at the speed measuring position on the transmission; the sleeve is provided with axial connecting teeth connected to the inner ring transmission friction pair, and the bearing sleeve is On the pillow block at the end of the main shaft of the transmission, the outer peripheral wall of the bearing is connected with the inner hole of the gear coupling so that it serves as a bearing seat; the gear coupling and the outer ring transmission sleeve are connected by connecting bolts; the outer ring transmission sleeve is provided with axial connecting teeth connected to the outer ring transmission friction pair; the fixed baffle is fixed on the outer ring transmission sleeve; the bearing gland fixes the bearing through the fastening bolts of the center hole of the reducer main shaft; the gear coupling and the outer ring transmission sleeve are connected by connecting bolts; one end of the protective cover is fixed on the transmission case, and the other end is suspended on the connecting shaft; a shaft seal is installed on the protective cover; the gear coupling is connected to the torque limiter through the connecting shaft, and the torque limiter is connected to the generator or load; the hydraulic station is connected to the rotary oil supply device through a pipeline.

3. A dual-power drive system using a hydraulic automatic clutch device according to claim 1 or 2, characterized in that: The control device is mainly composed of a PLC, which processes the signal sent from the speed difference sensor and issues instructions to other devices in the device. The PLC model is SIMATIC S7-1500.

Images