A quantitative heat load durability testing device for a flywheel and clutch system

Abstract

The present invention discloses a quantitative heat load durability detection device for a flywheel and a clutch system, comprising: a motor drives a main shaft and an inertia disc to rotate through a main shaft clutch; after the main shaft clutch is disengaged, a flywheel and a clutch sample are combined with the main shaft and the inertia disc through a combining device, and the clutch of the flywheel and the clutch sample slips and grinds to brake the main shaft and the inertia disc; the slip grinding energy is controlled by controlling the initial slip grinding speed and the moment of inertia; the slip grinding torque is controlled by the moment of inertia and the angular acceleration of the slip grinding deceleration; the measured slip grinding work is analyzed by monitoring the slip grinding torque and the slip grinding speed. The motor drives the main shaft and the inertia disc to rotate through the main shaft clutch. After the main shaft and the inertia disc reach the target speed, the main shaft clutch is disengaged, and the flywheel and the clutch sample are combined with the main shaft and the inertia disc; the main shaft and the inertia disc are braked by slip grinding; the above process is repeated to realize the durability test of the flywheel and the clutch, and the torque generated by the slip grinding of the flywheel and the clutch is measured by a torque measuring device.

Description

Technical Field

[0001] The present invention belongs to the technical field of commercial vehicle powertrain product testing, and particularly relates to a durability testing device for a flywheel and a clutch system with a quantitative thermal load, which simulates the sliding friction of the flywheel and the clutch, inputs a fixed sliding friction energy to the flywheel and the clutch input by controlling the inertia and speed, and then realizes the durability detection by controlling the part temperature. Background Art

[0002] The flywheel and the clutch are key structural components for vehicle power transmission. For their thermal fatigue failure, in addition to friction material tests, there are also single-part verification methods, system assembly verification methods, and vehicle durability verification. Since the single-part verification and system assembly verification structures are relatively complete, the test costs are relatively low, and the structural verification influencing factors are relatively few, they are better verification paths. However, due to the imperfect division of labor and related methods for the integrated matching of flywheel and clutch components, at present, the durability verification technologies for components and systems only have detection devices with different applicable conditions, most of which are clutch detection devices, and there is no flywheel thermal fatigue detection device.

[0003] There are two existing detection methods relatively close to the durability of the flywheel and clutch system.

[0004] Solution 1: It is the detection of the clutch driven disk components. By using a clutch driven disk torque characteristic test bench, the torque stiffness of the driven disk and the torsion angle corresponding to the maximum engine torque can be detected. Such as the "Schematic Diagram of Torsion Characteristic Test of Driven Disk Assembly" on page 7 of "QC / T 27-2014 Automotive Dry Friction Clutch Assembly Bench Test Method".

[0005] Solution 2: It is the detection of the clutch assembly. By using a clutch friction performance test bench, the starting inertia sliding friction and ramp resistance sliding friction can be simulated. When the tested clutch parts slide, a certain temperature rise will occur. When the tested clutch operates, mainly the static friction torque test and the sliding friction torque test are carried out. Such as the "Clutch Friction Performance Test Bench" on page 10 of "QC / T 27-2014 Automotive Dry Friction Clutch Assembly Bench Test Method".

[0006] The existing clutch system test benches have the following deficiencies in detecting the durability of the flywheel and clutch system:

[0007] The system verification conditions of the clutch driven disk torque characteristic test bench are insufficient: It only targets the torque characteristics of the driven disk and can only evaluate the torque characteristics of the driven disk under relative conditions. Since it does not have the same system structure conditions such as the clutch pressure plate and the flywheel, it ignores the influence of the pressure distribution of the pressure plate, the surface topography of the flywheel and the pressure plate on friction, and also lacks the condition of the working temperature of the driven disk. Therefore, the durability verification under the structural conditions of the flywheel and the clutch system cannot be carried out.

[0008] The clutch friction performance test bench has a complex system, high cost, and poor part temperature control conditions: This test bench of the scheme has a driving torque (motor) and a road resistance torque (brake), so it can better simulate the working mode of the transmission assembly. However, when the clutch is running, it is difficult to implement stable temperature control of the clutch. Moreover, the clutch temperature has a great influence on the sliding friction performance, adding uncertain factors to the thermal fatigue durability test. At the same time, the test bench requires inertia and braking control, and also requires a large motor to overcome the braking torque, so the operation control conditions are complex and the cost of the test bench is high. Summary of the Invention

[0009] Aiming at the problems existing in the background technology, the purpose of the present invention is to provide a flywheel and clutch system quantitative thermal load durability inspection device with a simple structure and low cost.

[0010] To achieve the above purpose, the flywheel and clutch system quantitative thermal load durability inspection device designed by the present invention includes: a motor, a main shaft clutch, a main shaft and an inertia disc, a flywheel and a clutch sample, a torque measurement device, and a temperature sensor;

[0011] The motor drives the main shaft and the inertia disc to rotate through the main shaft clutch; after the main shaft clutch is disengaged, the flywheel and the clutch sample are combined with the main shaft and the inertia disc through a combination device, and the clutch of the flywheel and the clutch sample slides and grinds to stop the main shaft and the inertia disc; the torque measurement device measures the torque generated by the sliding and grinding of the flywheel and the clutch; the temperature sensor measures the temperature of the flywheel and the clutch sample during the sliding and grinding process.

[0012] The sliding and grinding energy is controlled by controlling the initial sliding and grinding speed and the moment of inertia; the sliding and grinding torque is controlled by the moment of inertia and the angular acceleration of the sliding and grinding deceleration; the measured sliding and grinding work is analyzed by monitoring the sliding and grinding torque and the sliding and grinding speed.

[0013] Preferably, the motor acceleration torque is calculated by setting the shortest acceleration time for motor selection.

[0014] Preferably, the driving end of the main shaft clutch is connected to the output end of the motor, and the driven end of the main shaft clutch is connected to the main shaft and the inertia disc through a first main shaft connection flange.

[0015] Further preferably, a brake disc structure is provided at the driven end of the main shaft clutch.

[0016] Preferably, the main shaft and the inertia disc include a main shaft, and at least one inertia disc is coaxially fixed on the main shaft; both ends of the main shaft are respectively rotatably connected to a first main shaft bearing seat and a second main shaft bearing seat; the first main shaft bearing seat is located between the main shaft clutch and the inertia disc, and the second main shaft bearing seat is located between the inertia disc and the combination device.

[0017] Further preferably, for the strengthening test, the maximum inertia is designed according to 150% of the full-load condition of the whole vehicle.

[0018] Preferably, the dynamic balance quality level of the main shaft and the inertia disk is not lower than G2.5.

[0019] Preferably, the main shaft is designed to withstand a torque of 2.5 times the working torque as the impact torque.

[0020] Preferably, the coupling device includes a simulation shaft for simulating the first shaft of the gearbox; the simulation shaft is connected to the main shaft and the inertia disk through the second connecting flange of the main shaft; one end of the simulation shaft is inserted into the flywheel and the clutch sample.

[0021] Preferably, the flywheel and the clutch sample are rotatably mounted on a sample trolley that can move axially through a sample bearing seat.

[0022] Further preferably, one end of the sample bearing seat bears the flywheel and the clutch sample through a sample flange, and the other end of the sample bearing seat is circumferentially constrained by a force arm and a force sensor or a flange torque sensor.

[0023] The beneficial effects of the present invention are as follows: The motor drives the main shaft and the inertia disk to rotate through the main shaft clutch. After the main shaft and the inertia disk reach the target speed, the main shaft clutch disengages, and the flywheel and the clutch sample are combined with the main shaft and the inertia disk; the main shaft and the inertia disk are braked to a stop by skidding; the above process is repeated to realize the durability test of the flywheel and the clutch, and the torque generated by the skidding of the flywheel and the clutch is measured by a torque measuring device; the temperatures of the flywheel and the clutch are synchronously monitored, and the durability test of the flywheel and the clutch under stable temperature conditions can be realized through temperature monitoring.

[0024] By using the present invention, the temperature of the parts is established through the skidding of the flywheel and the clutch. After reaching the target temperature, the skidding is controlled, so that the parts can skid under stable temperature - starting temperature conditions. The energy of each skidding can be controlled by the rotational speed and the inertia, so that the part temperature and the skidding energy representing the thermal load of the flywheel and the clutch can be clearly controlled and measured through the skidding power analyzed by the part temperature, the skidding temperature rise, the skidding rotational speed and the skidding torque, providing reliable conditions for the quantitative thermal load durability detection of the flywheel and the clutch system. Description of the Drawings

[0025] Figure 1 is the structural schematic diagram of the present invention;

[0026] Figure 2 is the skidding principle diagram of the flywheel and the clutch of the present invention;

[0027] Figure 3 is the measured and analyzed skidding work of the present invention;

[0028] Figure 4Schematic diagram of the installation and torque detection structure of the flywheel and clutch sample of the present invention;

[0029] Figure 5 Schematic of the thermal fatigue test case of the flywheel and clutch of the present invention Figure 1 ;

[0030] Figure 6 Schematic of the thermal fatigue test case of the flywheel and clutch of the present invention Figure 2 。 Detailed implementation manners

[0031] The technical solutions (including the preferred technical solutions) of the present invention will be further described in detail below by means of the accompanying drawings and by listing some optional embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0032] As Figures 1 to 6 shown, the quantitative thermal load durability detection device for the flywheel and clutch system designed by the present invention includes: motor 1, main shaft clutch 2, brake disc structure 3, first main shaft connection flange 4, first main bearing seat 5, main shaft 6, inertia disc 7, inertia disc bracket 8, main shaft base 9, second main shaft bearing seat 10, second main shaft connection flange 11, simulation shaft 12, flywheel and clutch sample 13, sample bearing seat 14, torque measurement device 15, sample trolley 16, and measurement and control console 17. Motor speed n, electromagnetic clutch switch K1, electromagnetic clutch driven end speed n', first main bearing temperatures T1, T2 of the main shaft, sample switch K2, sample temperature T, and slip friction torque To.

[0033] The flywheel and clutch pressure plate of the flywheel and clutch sample 13 are installed and fixed on the sample trolley 16, and the clutch driven disc of the flywheel and clutch sample 13 is connected to the main shaft 6 and the inertia disc; in the separated state of the flywheel and clutch sample 13, the main shaft 6 and the inertia disc 7 are driven by the motor 1 through the main shaft clutch 2. After reaching the target speed, the main shaft clutch 2 is separated, the flywheel and clutch sample 13 is engaged, and the sample clutch and the flywheel slip friction to brake the main shaft 6 and the inertia disc 7. During the slip friction braking process, on the one hand, the mechanical energy of the structural system is converted into the heat energy of the flywheel and the clutch sample, and the temperature of the sample parts rises. On the other hand, the torque generated by the slip friction of the flywheel and the clutch is tested through the torque measurement structure, and thus the durability test of the flywheel and the clutch is realized repeatedly.

[0034] For the theoretical calculation of the slip friction of the flywheel and clutch system, see Figure 2, controlling the initial slip grinding rotational speed ω and the moment of inertia I can control the slip grinding energy E. The moment of inertia I and the angular acceleration β of slip grinding deceleration (i.e., the slip grinding time t2) can control the slip grinding torque T. Since the slip grinding generates part temperature rise, the part temperature can also be controlled. Therefore, the test structure can achieve a quantitative thermal load durability test; in addition, by designing the shortest acceleration time t1, the motor acceleration torque can be calculated, providing a basis for motor selection.

[0035] E = ω 2 ·I / 2 Equation 1;

[0036] T o = I·β / 2 Equation 2.

[0037] E is the slip grinding energy (J); To is the slip grinding torque (Nm); ω is the angular velocity (rad / s); β is the angular acceleration (rad / s 2 ); I is the moment of inertia (kgm 2 ); t1 is for acceleration, t2 is for braking, and t3 is for delay.

[0038] The present invention can monitor the slip grinding torque and the slip grinding rotational speed, analyze the measured slip grinding work. The analysis and calculation are shown in Equation 3, and the relevant description is shown in Figure 3 .

[0039]

[0040] Figure 1 is the structural schematic diagram of the present invention. The device monitors and controls the motor rotational speed, electromagnetic clutch switch (engagement and separation), spindle rotational speed, main bearing temperature, specimen switch (engagement and separation), specimen temperature, and slip grinding torque according to the structural principle.

[0041] As Figure 4 shown, the simulation shaft 12 is inserted into the clutch driven disk 13.1 for rotation. The flywheel 13.2 and the clutch pressure plate 13.3 are fixed on the specimen flange 18, and their circumferences are constrained by the torque detection device 15. When the clutch is separated, the driven disk and the spindle rotate. When the clutch is engaged, the driven disk and the spindle perform slip grinding braking, and the generated torque is measured by the torque detection device. The temperature sensor is connected to the thermocouple lead 22 and is used to measure the temperature of the flywheel and the clutch specimen during the slip grinding process.

[0042] In this way, the flywheel and the clutch specimen can perform slip grinding under certain temperature and certain slip grinding energy conditions, simulate the working process of the flywheel and the clutch, and obtain the detection of the specimen temperature and the system slip grinding parameters, thereby realizing a quantitative thermal load durability test.

[0043] The power drive of the present invention adopts a motor 1 and an electromagnetic clutch, i.e., a main shaft clutch 2 for driving. The driving end of the electromagnetic clutch is connected to the motor 1, the driven end of the electromagnetic clutch is connected to the first connection flange 4 of the main shaft, and a brake disc structure 3 is installed at the driven end; the measurement and control console 17 measures and controls the motor speed, the engagement and disengagement of the electromagnetic clutch, the speed of the driven end, and the braking.

[0044] In some alternative embodiments of the present invention, the main shaft and the inertia disc include a main shaft 6, and at least one inertia disc 7 is coaxially fixed on the main shaft 6; both ends of the main shaft 6 are respectively rotatably connected to a first main shaft bearing seat 5 and a second main shaft bearing seat 10; the first main shaft bearing seat 5 is located between the main shaft clutch 2 and the inertia disc 7, and the second main shaft bearing seat 10 is located between the inertia disc 10 and the coupling device.

[0045] The main shaft and inertia structure of the present invention adopt a structure supported by bearing seats at both ends and a combined inertia disc structure; the inertia discs 7 can be selected according to the test requirements, and a certain number of inertia discs 7 are installed on the main shaft 6, and the remaining inertia discs 7 are fixed on the inertia disc bracket 2; to ensure the coaxial assembly requirements of the main shaft and the inertia structure, the whole structure is installed on a main shaft base 9. To strengthen the test, the maximum inertia is designed according to 150% of the full load condition of the whole vehicle; to ensure reliability, the dynamic balance quality level of the main shaft and the inertia disc is not lower than G2.5 (refer to GB T9239.1-2006); the main shaft is designed to withstand an impact torque of 2.5 times the working torque (see Equation 2); the dynamic load of the main bearings is determined according to the G2.5 dynamic balance index and the working speed, and the type is selected accordingly; the measurement and control console monitors the working temperature and vibration of the main bearings and can set limit values for protection.

[0046] According to the structure of the clutch sample, a simulation shaft 12 simulating the first shaft of the transmission is designed, and the simulation shaft 12 is connected to the second connection flange 11 of the main shaft.

[0047] Installation and torque detection device for the flywheel and the clutch sample. The clutch driven disc 13.1 is fitted and inserted into the simulation shaft 12; the sample flange 18 is designed according to the dimensions of the flywheel housing 19 and the flywheel 13.2, and is axially and circumferentially positioned and connected. One end of the sample flange 18 is supported by the sample bearing seat 14, and the other end flange of the sample bearing seat 14 is constrained by the force arm and the force sensor to detect the impact sliding friction torque. The force arm + tension and compression sensor form can be adopted. The torque detection range is 50 Nm to 7000 Nm, and the force arm length is 50 to 90 cm. The tension and compression sensor is selected accordingly. The flange type torque sensor form can also be considered for detection; the clutch pressure plate 13.3 is fastened to the flywheel 13.2, the front housing 20 of the transmission is fitted and installed with the flywheel housing 19, and the clutch actuator 21 controls the engagement and disengagement of the clutch.

[0048] The sample bearing block 14 and the torque detection device 15 are installed on the sample trolley 16. The sample trolley 16 can move horizontally along the axis, facilitating the disassembly and assembly of the flywheel and clutch samples. The motor 1, the main shaft 6, and the sample bearing block 14 need to be installed with good alignment.

[0049] The present invention has good capabilities for verifying the thermal fatigue durability of sample temperature control and sliding friction work control.

[0050] For the thermal fatigue quality improvement verification work of a certain flywheel and clutch assembly of the company, durability tests were carried out using the present invention. The detection results of the relevant verification main parameters are shown in Figure 5 、 Figure 6 . The implementation and application can show that by using the present invention, the temperature of the parts is established through the sliding friction of the flywheel and the clutch. After reaching the target temperature, the sliding friction is controlled, so that the parts can perform sliding friction under the stable temperature - starting temperature condition. The energy of each sliding friction can be controlled by the rotational speed and inertia, enabling the part temperature and sliding friction energy, which characterize the thermal load of the flywheel and the clutch, to be clearly controlled and measured through the sliding friction power analyzed by the part temperature, sliding friction temperature rise, sliding friction rotational speed, and sliding friction torque, providing reliable conditions for the quantitative thermal load durability detection of the flywheel and clutch system.

[0051] Aiming at the problem of thermal fatigue verification under the conditions of the flywheel and clutch system, the present invention uses the conditions of inertia and rotational speed control to drive the rotation of the clutch driven disc, and then uses the sliding friction generated by the engagement of the clutch and the flywheel to simulate the sliding friction working condition of the clutch, and enables the parts to establish high-temperature conditions, providing test conditions for the quantitative thermal load durability of the flywheel and clutch system. The present invention drives the rotation of the driven disc, generates sliding friction with the flywheel and the clutch pressure plate supported by the bearing block and constrained by the force arm and the force sensor, and detects the structure of the sliding friction torque.

[0052] It is easy for those skilled in the art to understand that the above is only a preferred embodiment of the present invention and does not limit the present invention. Any modifications, combinations, substitutions, improvements, etc. made within the spirit and principle of the present invention are included in the protection scope of the present invention.

Claims

1. A quantitative heat load durability detection device for a flywheel and clutch system, characterized in that, Including: Motor, main shaft clutch, main shaft and inertia disc, flywheel and clutch sample, torque measuring device, temperature sensor; The main shaft and inertia disc include a main shaft, and at least one inertia disc is coaxially fixed on the main shaft; both ends of the main shaft are rotatably connected to a first main shaft bearing seat and a second main shaft bearing seat respectively; the first main shaft bearing seat is located between the main shaft clutch and the inertia disc, and the second main shaft bearing seat is located between the inertia disc and the coupling device; The motor drives the main shaft and inertia disc to rotate through the main shaft clutch; after the main shaft clutch is disengaged, the flywheel and clutch sample are coupled to the main shaft and inertia disc through the coupling device, and the clutch of the flywheel and clutch sample slips and grinds with the flywheel to brake the main shaft and inertia disc; the torque measuring device measures the torque generated by the slip and grind of the flywheel and clutch; the temperature sensor measures the temperature of the flywheel and clutch sample during the slip and grind process; Quantitative control of the slip and grind energy is achieved by controlling the initial slip and grind speed and the moment of inertia of the inertia disc; the slip and grind torque is controlled by the moment of inertia and the angular acceleration of the slip and grind deceleration; the measured slip and grind work is analyzed by monitoring the slip and grind torque and slip and grind speed; The flywheel and clutch sample are rotatably mounted on a sample trolley that can move axially through a sample bearing seat; One end of the sample bearing seat bears the flywheel and clutch sample through a sample flange, and the other end of the sample bearing seat is constrained by a force arm and a force sensor or circumferentially constrained by a flange type torque sensor.

2. The quantitative heat load durability detection device for the flywheel and clutch system according to claim 1, characterized in that: The acceleration torque of the motor is calculated by setting the shortest acceleration time for motor selection.

3. The quantitative heat load durability detection device for the flywheel and clutch system according to claim 1, wherein: The driving end of the main shaft clutch is connected to the output end of the motor, and the driven end of the main shaft clutch is connected to the main shaft and inertia disc through a first main shaft connection flange.

4. The quantitative heat load durability detection device for the flywheel and clutch system according to claim 3, wherein: The driven end of the main shaft clutch is provided with a brake disc structure.

5. The quantitative heat load durability detection device for the flywheel and clutch system according to claim 1, characterized in that: For enhanced testing, the maximum moment of inertia is designed according to 150% of the full vehicle load condition.

6. The quantitative heat load durability detection device for the flywheel and clutch system according to claim 1, wherein: The dynamic balance quality level of the main shaft and inertia disc is not lower than G2.5; the main shaft is designed to withstand a torque impact of 2.5 times the working torque.

7. The quantitative heat load durability detection device for the flywheel and clutch system according to claim 1, wherein: The coupling device includes a simulation shaft for simulating the first shaft of the gearbox; the simulation shaft is connected to the main shaft and inertia disc through a second main shaft connection flange; One end of the simulation shaft is inserted into the flywheel and clutch sample.

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