Rapid test system and method for thermal management efficiency of phase change flywheel

Abstract

The invention relates to a rapid test system and method for thermal management efficiency of a phase change flywheel, and the system comprises a flywheel test bench which comprises a rack, a main shaft rotatably connected to the rack, a split inertia disc fixed to the main shaft, and a motor connected to the main shaft through an electromagnetic clutch, and the motor drives the main shaft and the split inertia disc to rotate synchronously; the heat management unit comprises a phase change flywheel fixed on the rack, a clutch driven disc connected with the main shaft and matched with the phase change flywheel, and a clutch pressure disc connected to the phase change flywheel and used for controlling a friction gap between the clutch driven disc and the phase change flywheel; and the temperature monitoring unit comprises a first temperature sensor for measuring the temperature value of the clutch pressure plate, a second temperature sensor for measuring the temperature value of the phase change flywheel, and a controller for acquiring data acquired by the first temperature sensor and the second temperature sensor. Whether the phase-change material of the phase-change flywheel plays a latent heat role or not can be known, so that optimal matching development of the phase-change material in the phase-change flywheel is guided.

Description

Technical Field

[0001] The present application relates to the technical field of engine flywheel performance testing, and in particular to a rapid testing system and method for the thermal management efficiency of a phase change flywheel. Background Art

[0002] Flywheel thermal fatigue cracking is a difficult problem that needs to be overcome in commercial vehicle engine transmission systems. In related technologies, the high heat storage density of phase change materials is utilized to set a cavity filled with phase change materials in the flywheel to reduce the temperature peak of the flywheel during sliding friction, thereby achieving the purpose of avoiding thermal fatigue.

[0003] Since the thermal conductivity of phase change material is much lower than that of flywheel matrix material, when the temperature of flywheel matrix exceeds a certain temperature, the physical state of phase change material changes to absorb heat. However, when the absorbed heat reaches a certain amount, the filling of phase change material will inevitably deteriorate the heat dissipation capacity of flywheel.

[0004] To this end, it is necessary to test the temperature-rise characteristics of phase-change flywheels and determine the effectiveness of phase-change materials in reducing the temperature rise during the sliding friction of the flywheel when a specified energy input is applied. Currently, there is little experimental verification of the sliding friction temperature rise of phase-change flywheels under specified energy conditions. Design improvements can only be made based on market feedback, which results in long design cycles and relatively high design quality risks. Summary of the Invention

[0005] The embodiments of the present application provide a rapid testing system and method for the thermal management efficiency of a phase change flywheel to solve the problem that in related technologies, there is little experimental verification of the sliding friction heating process of the phase change flywheel under specified energy conditions, and design improvements can only be made based on market operation feedback, resulting in a long design cycle and relatively high risk of design quality.

[0006] A first aspect of an embodiment of the present application provides a rapid testing system for the thermal management efficiency of a phase change flywheel, comprising: A flywheel test bench, comprising a frame rotatably connected to a main shaft, a split inertia disc fixed to the main shaft, and a motor connected to the main shaft via an electromagnetic clutch, the motor driving the main shaft and the split inertia disc to rotate synchronously; a thermal management unit comprising a phase-change flywheel fixed to the frame, a clutch driven plate connected to the main shaft and in sliding and frictional engagement with the phase-change flywheel, and a clutch pressure plate connected to the phase-change flywheel for controlling a friction gap between the clutch driven plate and the phase-change flywheel; A temperature monitoring unit includes a first temperature sensor for measuring the temperature value of the clutch pressure plate, a second temperature sensor for measuring the temperature value of the phase change flywheel, and a controller for acquiring data collected by the first temperature sensor and the second temperature sensor.

[0007] In some embodiments, a spindle support seat is provided on the frame to support the rotation of the spindle, a bearing seat connected to the spindle is provided on the spindle support seat, and a lubricating oil cooling channel for cooling and lubricating the spindle and the bearing is provided on the bearing seat; The frame is provided with a sample support seat for mounting and fixing the phase change flywheel, and the sample support seat is provided with a flywheel fixing seat connected to the phase change flywheel. The axes of the flywheel fixing seat, the main shaft, the electromagnetic clutch and the motor are all coaxially arranged with each other.

[0008] In some embodiments: the clutch pressure plate is connected to a hydraulic operating mechanism that drives the clutch pressure plate to approach or move away from the clutch driven plate, and a displacement sensor that detects the contact gap between the clutch pressure plate and the clutch driven plate. The hydraulic operating mechanism, displacement sensor and electromagnetic clutch are all connected to the controller.

[0009] In some embodiments: the electromagnetic clutch includes an active end and a driven end, the active end is connected to the output shaft of the motor via an elastic coupling, and the driven end is connected to the main shaft via an interference fit through a shrink-fit process; The motor is a servo motor, which is connected to a rotation speed sensor and a torque sensor. The servo motor, the rotation speed sensor and the torque sensor are all connected to the controller.

[0010] In some embodiments, the first temperature sensor and the second temperature sensor are both thermocouple sensors, and a plurality of the second temperature sensors are embedded on a side of the phase change flywheel close to the flywheel friction surface, and the distance between the second temperature sensor and the flywheel friction surface is 0.5-1 mm; Multiple first temperature sensors are embedded on the side of the clutch pressure plate close to the friction surface of the pressure plate. The distance between the first temperature sensor and the friction surface of the pressure plate is 0.5-1mm. The lead of the first temperature sensor passes through the back of the clutch pressure plate into the main shaft and is connected to the controller through an electric slip ring.

[0011] In some embodiments: a honeycomb cavity filled with phase change material is formed at one end of the phase change flywheel away from the flywheel friction surface, the phase change material is filled in the honeycomb cavity, and a plug for sealing the honeycomb cavity is welded on the phase change flywheel; The temperature monitoring unit also includes an infrared thermal imager for measuring the temperature information of the end of the phase change flywheel facing away from the flywheel friction surface, the infrared thermal imager is connected to the controller, and a polycarbonate explosion-proof cabin covering the flywheel test bench, the infrared thermal imager is fixed on the top of the polycarbonate explosion-proof cabin.

[0012] In some embodiments: the split inertia disc is sleeved on the main shaft through the inner hole, the inner hole of the split inertia disc is provided with a plurality of key slots that engage with the main shaft, and the outer circumference of the split inertia disc is provided with a plurality of dovetail slots evenly distributed around the circumference, and each dovetail slot is embedded with a detachable counterweight block.

[0013] In some embodiments: the phase change flywheel and the clutch pressure plate are made of the same material, and both sides of the clutch driven plate are provided with friction plates that slide and frictionally cooperate with the phase change flywheel and the clutch pressure plate respectively, and the friction plates on both sides of the clutch driven plate are made of the same material.

[0014] A second aspect of the present application provides a method for rapidly testing the thermal management efficiency of a phase change flywheel. The method uses a system for rapidly testing the thermal management efficiency of a phase change flywheel as described in any of the above embodiments. The method includes: The clutch pressure plate connected to the first temperature sensor and the phase change flywheel connected to the second temperature sensor are installed on the flywheel test bench. The electromagnetic clutch is combined with the starter motor to drive the main shaft, the split inertia plate and the clutch driven plate to rotate synchronously. When the clutch driven disc speed is 850-1200 r / min, the braking inertia of the split inertia disc is 30-40 kg·m 2 When the cyclic sliding friction energy reaches 120~240kJ, the clutch pressure plate pushes the clutch driven plate and the phase change flywheel to slide for 2s / time~10s / time; The sliding friction starting temperature of the phase change flywheel, clutch pressure plate and clutch driven plate is designed to be a temperature point in the range of 5 to 20°C. The sliding friction temperature rise test is carried out from 180°C to 350°C, and each temperature point is cycled for 20 to 50 times. After each sliding friction test, the temperature of the phase change flywheel returns to the set sliding friction starting temperature before the next cycle; The controller synchronously collects the temperature values ​​of the phase change flywheel and the clutch pressure plate during each sliding process at a frequency of 20 to 50 times per second to obtain the starting temperature of the clutch pressure plate and the temperature rise peak values ​​of the clutch pressure plate and the phase change flywheel; Calculating the temperature rise of the clutch pressure plate and the phase change flywheel at each phase change flywheel sliding starting temperature cycle and obtaining an average value; The average value of the clutch pressure plate sliding wear starting temperature collected was used as the independent variable, and the average value of the clutch pressure plate temperature rise peak value was used as the dependent variable to fit and obtain the fitting formula; Finally, each temperature point set by the phase change flywheel is substituted into the fitting formula, and the temperature rise of the phase change flywheel is obtained by fitting calculation.

[0015] In some embodiments, the method further comprises: The temperature rise of the phase change flywheel obtained by fitting calculation is compared with the average temperature rise collected by actual measurement under the same conditions; When the temperature rise of the phase change flywheel obtained by fitting calculation is greater than the average temperature rise collected by actual measurement, it is judged that the phase change material has an inhibitory effect on the sliding wear temperature rise of the flywheel; When the temperature rise of the phase change flywheel obtained by fitting calculation is less than the average temperature rise collected by actual measurement, it is judged that the phase change material promotes the sliding temperature rise of the flywheel, which will deteriorate the thermal fatigue resistance of the flywheel; When the temperature rise of the phase change flywheel obtained by fitting calculation remains unchanged as the sliding starting temperature increases, it is judged that the latent heat of the phase change material plays a role in this temperature range.

[0016] The beneficial effects of the technical solution provided by this application include: An embodiment of the present application provides a rapid testing system and method for the thermal management efficiency of a phase change flywheel. Since the rapid testing system for the thermal management efficiency of a phase change flywheel of the present application is provided with a flywheel test bench, the flywheel test bench includes a frame, a main shaft rotatably connected to the frame, a split inertia plate fixed on the main shaft, a motor connected to the main shaft through an electromagnetic clutch, and the motor drives the main shaft and the split inertia plate to rotate synchronously; a thermal management unit, which includes a phase change flywheel fixed to the frame, a clutch driven plate connected to the main shaft and slidingly frictionally engaged with the phase change flywheel, and a clutch pressure plate connected to the phase change flywheel for controlling the friction gap between the clutch driven plate and the phase change flywheel; a temperature monitoring unit, which includes a first temperature sensor for measuring the temperature value of the clutch pressure plate, a second temperature sensor for measuring the temperature value of the phase change flywheel, and a controller for obtaining data collected by the first temperature sensor and the second temperature sensor.

[0017] Therefore, in the flywheel test bench of the rapid test system for the thermal management efficiency of the phase change flywheel of the present application, the main shaft connected to the frame is used to simulate the engine output shaft, the split inertia plate is used to simulate the flywheel connected to the engine, the electromagnetic clutch is used to simulate the clutch connecting the flywheel and the gearbox, and the motor is used to simulate the engine. When the motor rotates, the electromagnetic clutch is used to connect or disconnect the main shaft and the motor, so that the main shaft and the split inertia plate can reproduce the start-stop impact load of the flywheel, and provide power and energy for the phase change flywheel, clutch driven plate, and clutch pressure plate sliding wear test to set the speed and set the moment of inertia. The phase change flywheel is the test piece with phase change material configured inside, and the clutch driven plate and clutch pressure plate are the accompanying test pieces for the sliding wear test of the phase change flywheel. Controlling the number, speed, pressure and duration of sliding wear contact between these three can control the temperature change of the phase change flywheel for thermal management.

[0018] In addition, the first temperature sensor and the second temperature sensor are used to collect the clutch pressure plate temperature value and the phase change flywheel temperature value and transmit them to the controller. The controller synchronously collects the temperature values ​​of the phase change flywheel and the clutch pressure plate during each sliding process, obtains the starting temperature of the clutch pressure plate, the temperature rise peak values ​​of the clutch pressure plate and the phase change flywheel, and compares the temperature rise peak values ​​of the clutch pressure plate and the phase change flywheel to determine the temperature rise change of the phase change flywheel equipped with phase change material and the clutch pressure plate without phase change material. It can be known whether the phase change material of the phase change flywheel plays a latent heat role in a certain temperature range, thereby guiding the optimized matching development of the phase change material in the phase change flywheel. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0020] Figure 1 This is a schematic structural diagram of an embodiment of the present application; Figure 2 This is a diagram of the sliding wear test data processing in an embodiment of the present application.

[0021] Reference numerals: 1. Sample support base; 2. Phase change flywheel; 3. Clutch pressure plate; 4. Clutch driven plate; 5. Main shaft; 6. Split inertia plate; 7. Main shaft support base; 8. Electromagnetic clutch; 9. Motor; 10. First temperature sensor; 11. Second temperature sensor. DETAILED DESCRIPTION

[0022] To make the purpose, technical solutions, and advantages of the embodiments of this application more clear, the technical solutions in the embodiments of this application will be clearly and completely described below in conjunction with the drawings in the embodiments of this application. Obviously, the described embodiments are part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0023] The embodiments of the present application provide a rapid testing system and method for the thermal management efficiency of a phase change flywheel, which can solve the problem in related technologies that there is little experimental verification of the sliding friction heating process of the phase change flywheel under specified energy conditions, and design improvements can only be made based on market operation feedback, resulting in a long design cycle and relatively high risk of design quality.

[0024] See also Figure 1 As shown, the first aspect of the embodiment of the present application provides a rapid testing system for the thermal management efficiency of a phase change flywheel, comprising: The flywheel test bench includes a frame, on which a main shaft 5 is rotatably connected, a split inertia plate 6 fixed to the main shaft 5, and a motor 9 connected to the main shaft 5 via an electromagnetic clutch 8. The motor 9 drives the main shaft 5 and the split inertia plate 6 to rotate synchronously. The main shaft 5, split inertia plate 6, electromagnetic clutch 8, and motor 9 are arranged horizontally above the frame.

[0025] A thermal management unit includes a phase change flywheel 2 fixed on a frame, a clutch driven disc 4 connected to a main shaft 5 and slidingly frictionally engaged with the phase change flywheel 2, and a clutch pressure plate 3 connected to the phase change flywheel 2 for controlling the friction gap between the clutch driven disc 4 and the phase change flywheel 2. The clutch pressure plate 3 controls the friction gap and friction force between the clutch driven disc 4 and the phase change flywheel 2 by tightening or loosening the clutch driven disc 4.

[0026] The temperature monitoring unit includes a first temperature sensor 10 for measuring the temperature of the clutch pressure plate 3, a second temperature sensor 11 for measuring the temperature of the phase-change flywheel 2, and a controller for acquiring data collected by the first and second temperature sensors 10, 11. The first and second temperature sensors 10, 11 are used to monitor the slippage initiation temperature and peak temperature of the clutch pressure plate 3 and the phase-change flywheel 2, respectively.

[0027] In the flywheel test bench of the rapid test system for the thermal management efficiency of the phase change flywheel in the embodiment of the present application, the main shaft 5 rotatingly connected to the frame is used to simulate the engine output shaft, the split inertia plate 6 is used to simulate the flywheel connected to the engine, the electromagnetic clutch 8 is used to simulate the clutch connecting the flywheel and the gearbox, and the motor 9 is used to simulate the engine.

[0028] When the motor 9 is rotating, the electromagnetic clutch 8 is used to connect or separate the main shaft 5 and the motor 9, so that the main shaft 5 and the split inertia plate 6 can reproduce the start-stop impact load of the flywheel, and provide power and energy for the phase change flywheel 2, the clutch driven plate 4, and the clutch pressure plate 3 sliding wear test to set the speed and set the moment of inertia.

[0029] The phase change flywheel 2 is a test piece with phase change material configured inside, and the clutch driven plate 4 and the clutch pressure plate 3 are companion test pieces for the sliding wear test of the phase change flywheel 2. Controlling the number, speed, pressure and duration of sliding wear contact between the three can control the temperature change of the phase change flywheel 2 for thermal management.

[0030] In addition, the first temperature sensor 10 and the second temperature sensor 11 are used to collect the temperature values ​​of the clutch driven plate 4 and the phase change flywheel 2 and transmit them to the controller. The controller synchronously collects the temperature values ​​of the phase change flywheel 2 and the clutch pressure plate 3 during each sliding process to obtain the starting temperature of the clutch pressure plate 3 and the peak temperature rise of the clutch pressure plate 3 and the phase change flywheel 2.

[0031] By comparing the peak values ​​of the temperature rise of the clutch pressure plate 3 and the phase change flywheel 2, the controller can determine the temperature rise change of the phase change flywheel 2 equipped with phase change material and the clutch pressure plate 3 not equipped with phase change material. It can be known whether the phase change material of the phase change flywheel 2 plays a latent heat role in a certain temperature range, thereby guiding the optimized matching development of the phase change material in the phase change flywheel.

[0032] In some alternative embodiments: See Figure 1 As shown, an embodiment of the present application provides a rapid testing system for the thermal management efficiency of a phase change flywheel. The frame of the rapid testing system is provided with a spindle support seat 7 for supporting the rotation of a spindle 5. A bearing seat connected to the spindle 5 is provided on the spindle support seat 7. The spindle 5 is rotatably connected to the bearing seat via a bearing. A lubricating oil cooling flow channel is provided on the bearing seat to cool and lubricate the spindle 5 and the bearing. When lubricating oil is passed into the lubricating oil cooling flow channel, it not only lubricates the bearing but also cools the bearing and the spindle 5.

[0033] A sample support seat 1 for mounting and fixing the phase change flywheel 2 is provided on the frame, and a flywheel fixing seat connected to the phase change flywheel 2 is provided on the sample support seat. A mounting hole for connecting the phase change flywheel 2 is opened on the flywheel fixing seat, and the phase change flywheel is fixedly connected to the flywheel fixing seat by bolts. The axes of the flywheel fixing seat, the main shaft 5, the electromagnetic clutch 8 and the motor 9 are all coaxially arranged with each other.

[0034] The clutch pressure plate 3 is connected to a hydraulic operating mechanism (not shown in the figure) that drives the clutch pressure plate 3 to approach or move away from the clutch driven plate 4, and a displacement sensor (not shown in the figure) that detects the contact gap between the clutch pressure plate 3 and the clutch driven plate 4. The hydraulic operating mechanism, the displacement sensor and the electromagnetic clutch 8 are all connected to the controller.

[0035] The controller controls electromagnetic clutch 8 to disconnect motor 9 from spindle 5 while simultaneously controlling the hydraulic operating mechanism to gradually drive clutch pressure plate 3, pressing clutch driven plate 4 into contact with phase-change flywheel 2. A displacement sensor provides real-time feedback on the contact gap between clutch pressure plate 3 and clutch driven plate 4. The closed-loop control accuracy of the displacement sensor is ±0.05 mm.

[0036] The hydraulic operating mechanism drives the piston rod of the clutch pressure plate 3 at a speed of 0.5 mm / s, and the contact gap between the clutch pressure plate 3 and the clutch driven plate 4 is fed back in real time through the displacement sensor; when the contact gap between the clutch pressure plate 3 and the clutch driven plate 4 reaches 0.1 mm, the controller automatically switches to pressure control mode to maintain the clamping force within the range of 1.2 kN±5%.

[0037] In some alternative embodiments: See Figure 1 As shown, an embodiment of the present application provides a rapid testing system for the thermal management efficiency of a phase change flywheel. The electromagnetic clutch 8 of this rapid testing system includes an active end and a passive end. The active end is connected to the output shaft of the motor 9 via an elastic coupling, and the passive end is connected to the main shaft 5 via an interference fit through a shrink-fit process. The motor 9 is preferably a servo motor, which is connected to a speed sensor (not shown) and a torque sensor (not shown). The servo motor, speed sensor, and torque sensor are all connected to a controller. The servo motor's output speed is frequency-controlled by the controller to simulate the speed fluctuations of the flywheel under actual operating conditions.

[0038] In some alternative embodiments: See Figure 1 As shown, an embodiment of the present application provides a rapid testing system for the thermal management efficiency of a phase change flywheel. The first temperature sensor 10 and the second temperature sensor 11 of the rapid testing system are preferably thermocouple sensors. A plurality of second temperature sensors 11 are buried on one side of the phase change flywheel 2 close to the flywheel friction surface. The distance between the second temperature sensor 11 and the flywheel friction surface is 0.5-1 mm, so as to accurately measure the temperature value of the flywheel friction surface on the phase change flywheel 2.

[0039] Multiple first temperature sensors 10 are embedded on the clutch pressure plate 3, near the friction surface. The distance between the first temperature sensors 10 and the friction surface is 0.5-1 mm, ensuring accurate measurement of the temperature of the friction surface. The main shaft 5 is hollow. The leads of the first temperature sensors 10 pass through the back of the clutch pressure plate 3 and into the main shaft 5. They are connected to the controller via an electrical slip ring (not shown). The electrical slip ring rotates to connect the leads of the first temperature sensors 10, transmitting the electrical signals from the first temperature sensors 10, which rotate with the clutch pressure plate 3, to the controller.

[0040] In some alternative embodiments: See Figure 1 As shown, an embodiment of the present application provides a rapid testing system for the thermal management efficiency of a phase-change flywheel. This rapid testing system includes a honeycomb cavity filled with phase-change material on the end of the phase-change flywheel 2 facing away from the flywheel friction surface. The honeycomb cavity contains a network of microchannels with a diameter of 0.5 mm, which enhances heat conduction between the phase-change material and the phase-change flywheel 2. The phase-change material is filled in the honeycomb cavity, and a plug is welded to the phase-change flywheel 2 to seal the honeycomb cavity, further encapsulating the phase-change material within the honeycomb cavity.

[0041] The temperature monitoring unit also includes an infrared thermal imager (not shown) that measures the temperature of the end of the phase-change flywheel 2 facing away from the flywheel friction surface. This infrared thermal imager is connected to the controller and determines whether the phase-change material has leaked out of the flywheel 2 by measuring the temperature at this end. It also includes a polycarbonate explosion-proof cabin (not shown) that covers the flywheel test bench. This cabin serves as a safety shield, positioned around the perimeter of the flywheel test bench during testing to prevent parts from scattering. The infrared thermal imager is affixed to the top of the cabin.

[0042] In some alternative embodiments: See Figure 1 As shown, an embodiment of the present application provides a rapid testing system for the thermal management efficiency of a phase change flywheel. The split inertia disc 6 of the rapid testing system is sleeved on the main shaft 5 through an inner hole. The inner hole circumference of the split inertia disc 6 is provided with a plurality of key slots that engage with the main shaft 5. The outer circumference of the split inertia disc 6 is provided with a plurality of dovetail slots (not shown in the figure) evenly distributed around the circumference. A detachable counterweight block (not shown in the figure) is embedded in each dovetail slot.

[0043] The dovetail grooves on the outer periphery of the split inertia disc 6 are used to embed removable counterweights. The counterweights are radially compressed using a pneumatic clamp with an operating pressure of 0.6 to 1.2 MPa and a response time of ≤0.3 s. The moment of inertia of the split inertia disc 6 can be continuously adjusted between 5 and 50 kg·m² by adding or removing the counterweights.

[0044] In some alternative embodiments: See Figure 1 As shown, an embodiment of the present application provides a rapid testing system for the thermal management performance of a phase change flywheel. The phase change flywheel 2 and the clutch pressure plate 3 of the rapid testing system are made of the same material, which is selected from one of HT250, RuT450, and RuT500. A cavity filled with a phase change material is provided in the phase change flywheel 2, and the phase change point of the phase change material is 230~280°C. The material of the clutch pressure plate 3 is uniform, and no cavity is provided. Both sides of the clutch driven plate 4 are provided with friction plates that respectively slide and frictionally cooperate with the phase change flywheel 2 and the clutch pressure plate 3, and the friction plates on both sides of the clutch driven plate 4 are made of the same material.

[0045] The phase change flywheel 2 and the clutch pressure plate 3 of the embodiment of the present application are made of the same material, and the friction plates that contact the phase change flywheel 2 and the clutch pressure plate 3 respectively are made of the same material. Therefore, when the friction plates are tested for sliding friction with the phase change flywheel 2 and the clutch pressure plate 3, the heat values ​​generated by the mutual sliding friction tend to be the same, thereby more objectively evaluating, comparing and analyzing the latent heat effect of the phase change flywheel 2 configured with phase change material.

[0046] See also Figure 1 and Figure 2 As shown, the second aspect of the present application embodiment provides a method for rapidly testing the thermal management efficiency of a phase change flywheel. The method uses a rapid testing system for the thermal management efficiency of a phase change flywheel as described in any of the above embodiments, and the method includes: Step 1: Install the clutch pressure plate 3 connected to the first temperature sensor 10 and the phase change flywheel 2 connected to the second temperature sensor 11 on the flywheel test bench, combine with the electromagnetic clutch 8, and start the motor 9 to drive the main shaft 5, the split inertia plate 6 and the clutch driven plate 4 to rotate synchronously.

[0047] Step 2: When the speed of the clutch driven disc 4 is 850~1200r / min and the braking inertia of the split inertia disc 6 is 30~40kg·m 2 When the circulating sliding friction energy reaches 120~240kJ, the clutch pressure plate 3 pushes the clutch driven plate 4 and the phase change flywheel 2 to slide for 2s / time~10s / time.

[0048] Step 3: The starting temperature of the sliding friction of the phase change flywheel 2, the clutch pressure plate 3 and the clutch driven plate 4 is designed to be a temperature point in the range of 5 to 20°C. The sliding friction temperature rise test is carried out from 180°C to 350°C, and each temperature point is tested 20 to 50 times in a cycle.

[0049] Step 4: After each sliding friction test, the temperature of the phase change flywheel 2 is restored to the set sliding friction starting temperature before the next cycle is carried out.

[0050] Step 5: The controller synchronously collects the temperature values ​​of the phase change flywheel 2 and the clutch pressure plate 3 during each sliding process at a frequency of 20 to 50 times per second to obtain the starting temperature of the clutch pressure plate 3 and the temperature rise peak values ​​of the clutch pressure plate 3 and the phase change flywheel 2.

[0051] Step 6: The controller calculates the temperature rise of the clutch pressure plate 3 and the phase change flywheel 2 in each phase change flywheel 2 sliding start temperature cycle and obtains the average value.

[0052] Step 7: Using the collected average value of the clutch pressure plate 3 sliding start temperature as the independent variable and the average value of the clutch pressure plate 3 temperature rise peak value as the dependent variable, a fitting formula is obtained.

[0053] Step 8: Substitute each temperature point set for the phase change flywheel 2 into the fitting formula, and obtain the temperature rise of the phase change flywheel 2 through fitting calculation.

[0054] Step 9: Compare the temperature rise of the phase change flywheel obtained by fitting calculation with the average temperature rise value collected by actual measurement under the same conditions.

[0055] Step 10: When the temperature rise of the phase change flywheel 2 obtained by fitting calculation is greater than the average temperature rise value collected by actual measurement, it is determined that the phase change material has an inhibitory effect on the sliding wear temperature rise of the flywheel.

[0056] Step 11: When the temperature rise of the phase change flywheel 2 obtained by fitting calculation is less than the average temperature rise value collected by actual measurement, it is determined that the phase change material promotes the sliding temperature rise of the flywheel, which will deteriorate the thermal fatigue resistance of the flywheel.

[0057] Step 12: When the temperature rise of the phase change flywheel 2 obtained by fitting calculation remains unchanged as the sliding starting temperature increases, it is determined that the latent heat of the phase change material takes effect in this temperature range.

[0058] Specifically, the embodiment of the present application is described by taking the phase change point of the phase change material as 230° C. and the materials of the clutch pressure plate 3 and the phase change flywheel 2 as HT250 as an example.

[0059] The initial speed of the clutch driven plate 4 during the sliding process is controlled to be 850 r / min, the braking inertia of the split inertia plate 6 is 30 kg·m2, the cyclic sliding energy is 236 kJ / time, the sliding time is 2 s / time, and the sliding starting temperature of the phase change flywheel 2 is designed to have a step size of 20°C. The sliding temperature rise test is carried out from 180°C to 260°C, and each temperature point is tested 20 times in a cycle.

[0060] After each sliding operation, the next cycle is performed after the temperature of the phase change flywheel 2 returns to the set sliding start temperature.

[0061] The temperature changes of the phase change flywheel 2 and the clutch pressure plate 3 during each sliding process are synchronously collected at a frequency of 30 times / s to obtain the starting temperature of the clutch pressure plate 3 and the sliding temperature rise peak values ​​of the clutch pressure plate 3 and the phase change flywheel 2.

[0062] The temperature measuring points of the first temperature sensor 10 and the second temperature sensor 11 are respectively 1 mm apart from the friction surface of the clutch pressure plate 3 and the friction surface of the flywheel 2, and are both arranged in the metal substrate.

[0063] Calculate the temperature rise of the phase change flywheel 2 and the clutch pressure plate 3 under each phase change flywheel 2 sliding starting temperature cycle and calculate the average value, as shown in the following table:

[0064] The average value of the clutch pressure plate 3 sliding wear starting temperature collected is used as the independent variable, and the average value of the clutch pressure plate 3 temperature rise peak is used as the dependent variable for fitting, and the fitting formula y = 0.0029x 2 - 1.7342x + 294.05.

[0065] Then, each temperature point set by the phase change flywheel 2 is substituted into the fitting formula to obtain the temperature rise of the phase change flywheel obtained by fitting calculation.

[0066] The temperature rise of the phase change flywheel obtained by fitting calculation is compared with the average temperature rise actually collected under the same conditions.

[0067] Since the temperature rise of the phase change flywheel obtained by fitting calculation is greater than the average value of the collected temperature rise, it is judged that when the sliding friction starting temperature is lower than 237.8°C, the phase change material has an inhibitory effect on the sliding friction temperature rise of the phase change flywheel 2.

[0068] Since the temperature rise of the phase change flywheel obtained by fitting correction is less than the average value of the collected temperature rise, it is judged that when the sliding starting temperature is higher than 237.8°C, the phase change material promotes the sliding temperature rise of the phase change flywheel 2, which will deteriorate the thermal fatigue resistance of the phase change flywheel 2.

[0069] As the sliding friction starting temperature increases, the temperature rise of the phase change flywheel obtained by fitting calculation remains unchanged at about 5°C, indicating that when the sliding friction starting temperature is between 205.9 and 218°C, the latent heat of the phase change material plays a role in this temperature range.

[0070] Specifically, another embodiment of the present application is described by taking the phase change point of the phase change material as 278° C. and the materials of the clutch pressure plate 3 and the phase change flywheel 2 as RuT450 as an example.

[0071] The initial speed of the clutch driven plate 4 during the sliding process is controlled to be 1000 r / min, the braking inertia of the split inertia plate 6 is 35 kg·m2, the cyclic sliding energy is 259 kJ / time, the sliding time is 10 s / time, and the sliding starting temperature of the phase change flywheel 2 is designed to have a step size of 10°C. The sliding temperature rise test is carried out from 220°C to 350°C, and each temperature point is tested 30 times.

[0072] After each sliding operation, the next cycle is performed after the temperature of the phase change flywheel 2 returns to the set sliding start temperature.

[0073] The temperature changes of the phase change flywheel 2 and the clutch pressure plate 3 during each sliding process are synchronously collected at a frequency of 30 times / s to obtain the starting temperature of the clutch pressure plate 3 and the sliding temperature rise peak values ​​of the clutch pressure plate 3 and the phase change flywheel 2.

[0074] The temperature measuring points of the first temperature sensor 10 and the second temperature sensor 11 are respectively 0.5 mm apart from the friction surface of the clutch pressure plate 3 and the friction surface of the flywheel 2, and are both arranged in the metal substrate.

[0075] Calculate the temperature rise of the phase change flywheel 2 and the clutch pressure plate 3 each time the phase change flywheel 2 is in the sliding friction starting temperature cycle and calculate the average value.

[0076] The average value of the clutch pressure plate 3 sliding wear starting temperature collected is used as the independent variable, and the average value of the clutch pressure plate 3 temperature rise peak is used as the dependent variable for fitting, and the fitting formula y = 0.0037x 2 - 1.4326x + 339.47.

[0077] Then, each temperature point set by the phase change flywheel 2 is substituted into the fitting formula to obtain the temperature rise of the phase change flywheel obtained by fitting calculation.

[0078] The temperature rise of the phase change flywheel obtained by fitting calculation is compared with the average temperature rise actually collected under the same conditions.

[0079] Since the temperature rise of the phase change flywheel obtained by fitting calculation is greater than the average value of the collected temperature rise, it is judged that when the sliding friction starting temperature is lower than 295.4°C, the phase change material has an inhibitory effect on the sliding friction temperature rise of the phase change flywheel 2.

[0080] Since the temperature rise of the phase change flywheel obtained by fitting correction is less than the average value of the collected temperature rise, it is judged that when the sliding friction starting temperature is higher than 295.4°C, the phase change material promotes the sliding friction temperature rise effect of the phase change flywheel 2, which will deteriorate the thermal fatigue resistance of the phase change flywheel 2.

[0081] As the sliding friction starting temperature increases, the temperature rise of the phase change flywheel obtained by fitting calculation remains unchanged at about 5°C, indicating that when the sliding friction starting temperature is between 254.8 and 273.2°C, the latent heat of the phase change material plays a role in this temperature range.

[0082] How it works An embodiment of the present application provides a rapid testing system and method for the thermal management efficiency of a phase change flywheel. Since the rapid testing system for the thermal management efficiency of a phase change flywheel of the present application is provided with a flywheel test bench, the flywheel test bench includes a frame on which a main shaft 5 is rotatably connected, a split inertia plate 6 fixed on the main shaft 5, a motor 9 connected to the main shaft 5 through an electromagnetic clutch 8, and the motor 9 drives the main shaft 5 and the split inertia plate 6 to rotate synchronously; a thermal management unit, which includes a phase change flywheel 2 fixed on the frame, a clutch driven plate 4 connected to the main shaft 5 and slidingly frictionally engaged with the phase change flywheel 2, and a clutch pressure plate 3 connected to the phase change flywheel 2 for controlling the friction gap between the clutch driven plate 4 and the phase change flywheel 2; a temperature monitoring unit, which includes a first temperature sensor 10 for measuring the temperature value of the clutch pressure plate 3, a second temperature sensor 11 for measuring the temperature value of the phase change flywheel 2, and a controller for obtaining data collected by the first temperature sensor 10 and the second temperature sensor 11.

[0083] Therefore, in the flywheel test bench of the present application's rapid testing system for the thermal management performance of a phase-change flywheel, a main shaft 5 rotatingly connected to the frame simulates the engine output shaft, a split inertia plate 6 simulates the flywheel connected to the engine, an electromagnetic clutch 8 simulates the clutch connecting the flywheel and the gearbox, and a motor 9 simulates the engine. As the motor 9 rotates, the electromagnetic clutch 8 engages or disengages the main shaft 5 and motor 9, allowing the main shaft 5 and split inertia plate 6 to replicate the flywheel's start-stop impact loads and provide power and energy for the phase-change flywheel 2, clutch driven plate 4, and clutch pressure plate 3 to perform sliding wear tests at set speeds and set moments of inertia. The phase-change flywheel 2 is the test piece internally configured with phase-change material, while the clutch driven plate 4 and clutch pressure plate 3 serve as the companion test pieces for the sliding wear test of the phase-change flywheel 2. Controlling the number, speed, pressure, and duration of sliding wear contact between these three components can control the temperature changes of the phase-change flywheel 2 for thermal management.

[0084] In addition, the first temperature sensor 10 and the second temperature sensor 11 are used to collect the temperature values ​​of the clutch pressure plate 3 and the phase change flywheel 2 and transmit them to the controller. The controller synchronously collects the temperature values ​​of the phase change flywheel 2 and the clutch pressure plate 3 during each sliding process, obtains the starting temperature of the clutch pressure plate 3, the temperature rise peak values ​​of the clutch pressure plate 3 and the phase change flywheel 2, and compares the temperature rise peak values ​​of the clutch pressure plate 3 and the phase change flywheel 2 to determine the temperature rise change of the phase change flywheel 2 equipped with phase change material and the clutch pressure plate 3 without phase change material. It can be known whether the phase change material of the phase change flywheel 2 plays a latent heat role in a certain temperature range, thereby guiding the optimization matching development of the phase change material in the phase change flywheel 2.

[0085] In the description of this application, it should be noted that the terms "upper" and "lower" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application. Unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be internal communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0086] It should be noted that, in this application, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device comprising a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "comprising a ..." does not exclude the presence of other identical elements in the process, method, article or device comprising the element.

[0087] The foregoing is merely a list of specific embodiments of the present application, intended to enable those skilled in the art to understand or implement the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application is not limited to the embodiments shown herein, but is intended to conform to the broadest scope consistent with the principles and novel features of the present application.

Claims

1. A rapid testing system for the thermal management performance of a phase change flywheel, characterized in that: include: A flywheel test bench, comprising a frame, a main shaft (5) being rotatably connected to the frame, a split inertia disc (6) fixed to the main shaft (5), a motor (9) connected to the main shaft (5) via an electromagnetic clutch (8), and the motor (9) driving the main shaft (5) and the split inertia disc (6) to rotate synchronously; A thermal management unit, the thermal management unit comprising a phase change flywheel (2) fixed to the frame, a clutch driven disc (4) connected to the main shaft (5) and slidingly frictionally engaged with the phase change flywheel (2), and a clutch pressure plate (3) connected to the phase change flywheel (2) for controlling the friction gap between the clutch driven disc (4) and the phase change flywheel (2); A temperature monitoring unit, comprising a first temperature sensor (10) for measuring the temperature value of the clutch pressure plate (3), a second temperature sensor (11) for measuring the temperature value of the phase change flywheel (2), and a controller for acquiring data collected by the first temperature sensor (10) and the second temperature sensor (11).

2. The rapid testing system for thermal management performance of a phase change flywheel according to claim 1, characterized in that: The frame is provided with a spindle support seat (7) for supporting the rotation of the spindle (5), the spindle support seat (7) is provided with a bearing seat connected to the spindle (5), and the bearing seat is provided with a lubricating oil cooling channel for cooling and lubricating the spindle (5) and the bearing; The frame is provided with a sample support seat (1) for mounting and fixing the phase change flywheel (2), and the sample support seat (1) is provided with a flywheel fixing seat connected to the phase change flywheel (2), and the axes of the flywheel fixing seat, the main shaft (5), the electromagnetic clutch (8) and the motor (9) are all coaxially arranged with each other.

3. The rapid testing system for thermal management performance of a phase change flywheel according to claim 1, characterized in that: The clutch pressure plate (3) is connected to a hydraulic operating mechanism for driving the clutch pressure plate (3) to approach or move away from the clutch driven plate (4), and a displacement sensor for detecting a contact gap between the clutch pressure plate (3) and the clutch driven plate (4). The hydraulic operating mechanism, the displacement sensor and the electromagnetic clutch (8) are all connected to the controller.

4. The rapid testing system for thermal management performance of a phase change flywheel according to claim 1, characterized in that: The electromagnetic clutch (8) comprises an active end and a driven end, the active end is connected to the output shaft of the motor (9) via an elastic coupling, and the driven end is connected to the main shaft (5) via an interference fit using a shrink-fit process; The motor (9) is a servo motor, the servo motor is connected to a speed sensor and a torque sensor, and the servo motor, the speed sensor and the torque sensor are all connected to the controller.

5. The rapid testing system for thermal management performance of a phase change flywheel according to claim 1, characterized in that: The first temperature sensor (10) and the second temperature sensor (11) are both thermocouple sensors. A plurality of the second temperature sensors (11) are embedded on one side of the phase change flywheel (2) close to the flywheel friction surface. The distance between the second temperature sensor (11) and the flywheel friction surface is 0.5-1 mm. A plurality of first temperature sensors (10) are embedded on one side of the clutch pressure plate (3) close to the pressure plate friction surface, the first temperature sensor (10) is 0.5-1 mm away from the pressure plate friction surface, and the lead wires of the first temperature sensors (10) are passed through the back side of the clutch pressure plate (3) into the main shaft (5) and are connected to the controller through an electric slip ring.

6. The rapid testing system for thermal management performance of a phase change flywheel according to claim 1, characterized in that: A honeycomb cavity filled with phase change material is provided at one end of the phase change flywheel (2) facing away from the flywheel friction surface, the phase change material is filled in the honeycomb cavity, and a plug for sealing the honeycomb cavity is welded on the phase change flywheel (2); The temperature monitoring unit further comprises an infrared thermal imager for measuring temperature information of an end of the phase change flywheel (2) facing away from the flywheel friction surface, the infrared thermal imager being connected to the controller, and a polycarbonate explosion-proof cabin covering the flywheel test bench, the infrared thermal imager being fixed on the top of the polycarbonate explosion-proof cabin.

7. The rapid testing system for thermal management performance of a phase change flywheel according to claim 1, characterized in that: The split inertia disc (6) is sleeved on the main shaft (5) through the inner hole, and the inner hole circumference of the split inertia disc (6) is provided with a plurality of key slots meshing with the main shaft (5), and the outer circumference of the split inertia disc (6) is provided with a plurality of dovetail slots evenly distributed around the circumference, and each dovetail slot is embedded with a detachable counterweight block.

8. The rapid testing system for thermal management performance of a phase change flywheel according to claim 1, characterized in that: The phase change flywheel (2) and the clutch pressure plate (3) are made of the same material, and friction plates are provided on both sides of the clutch driven plate (4) for sliding and frictionally cooperating with the phase change flywheel (2) and the clutch pressure plate (3), respectively. The friction plates on both sides of the clutch driven plate (4) are made of the same material.

9. A rapid test method for the thermal management performance of a phase change flywheel, characterized in that: The method uses a rapid testing system for thermal management performance of a phase change flywheel according to any one of claims 1 to 8, and the method comprises: A clutch pressure plate (3) connected to a first temperature sensor (10) and a phase change flywheel (2) connected to a second temperature sensor (11) are mounted on a flywheel test bench, and combined with an electromagnetic clutch (8), a starting motor (9) drives the main shaft (5), the split inertia plate (6) and the clutch driven plate (4) to rotate synchronously; When the speed of the clutch driven disc (4) is 850-1200 r / min, the braking inertia of the split inertia disc (6) is 30-40 kg·m 2 When the cyclic sliding friction energy reaches 120-240 kJ, the clutch pressure plate (3) pushes the clutch driven plate (4) and the phase change flywheel (2) to slide for a time of 2 s / time to 10 s / time; The sliding friction starting temperature of the phase change flywheel (2), the clutch pressure plate (3) and the clutch driven plate (4) is designed to be a temperature point in the range of 5 to 20°C, and the sliding friction temperature rise test is carried out from 180°C to 350°C, and each temperature point is tested 20 to 50 times in a cycle; After each sliding friction test, the temperature of the phase change flywheel (2) is restored to the set sliding friction starting temperature before the next cycle is carried out; The controller synchronously collects the temperature values ​​of the phase change flywheel (2) and the clutch pressure plate (3) during each sliding process, with a collection frequency of 20 to 50 times / s, to obtain the starting temperature of the clutch pressure plate (3) and the temperature rise peak values ​​of the clutch pressure plate (3) and the phase change flywheel (2); Calculating the temperature rise of the clutch pressure plate (3) and the phase change flywheel (2) at each sliding start temperature cycle of the phase change flywheel (2) and obtaining an average value; The average value of the sliding wear starting temperature of the clutch pressure plate (3) collected is used as the independent variable, and the average value of the temperature rise peak of the clutch pressure plate (3) is used as the dependent variable to perform fitting to obtain a fitting formula; Finally, each temperature point set by the phase change flywheel (2) is substituted into the fitting formula, and the temperature rise of the phase change flywheel (2) is obtained by fitting calculation.

10. A rapid testing method for thermal management performance of a phase change flywheel according to claim 9, characterized in that: The method further comprises: The temperature rise of the phase change flywheel (2) obtained by fitting calculation is compared with the average temperature rise value collected by actual measurement under the same conditions; When the temperature rise of the phase change flywheel (2) obtained by fitting calculation is greater than the average temperature rise value collected by actual measurement, it is judged that the phase change material has an inhibitory effect on the sliding wear temperature rise of the flywheel; When the temperature rise of the phase change flywheel (2) obtained by fitting calculation is less than the average temperature rise value collected by actual measurement, it is judged that the phase change material promotes the sliding temperature rise effect of the flywheel, which will deteriorate the thermal fatigue resistance of the flywheel; When the temperature rise of the phase change flywheel (2) obtained by fitting calculation remains unchanged as the sliding starting temperature increases, it is judged that the latent heat of the phase change material plays a role in this temperature range.

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