Friction testing machine and testing method for elevator traction sheave under micro-motion working condition

Abstract

The invention discloses a friction testing machine and a friction testing method for an elevator traction sheave under a micro-motion working condition, and relates to the technical field of elevator traction sheave tests.The friction testing machine comprises a workbench, a traction motor and a plurality of steel wire ropes, and an output shaft of the traction motor is coaxially provided with the traction sheave; a guide wheel is rotatably arranged on the workbench, a tensioning wheel is slidably arranged on the workbench, the moving direction of the tensioning wheel is parallel to the Z-axis direction, and the central axis of the tensioning wheel, the central axis of the guide wheel and the central axis of the traction wheel are parallel to one another; a plurality of steel wire ropes are wound on the tensioning wheel, the guide wheel and the traction wheel; the tensioning wheel is further in transmission connection with a telescopic mechanism enabling the tensioning wheel to move in the Z-axis direction. A control mechanism used for controlling the traction motor to slightly move on the workbench in the Y-axis direction is further arranged on the workbench. Through a simulation test, the stress state of the traction sheave in the test process can be controlled in combination with controllable temperature, controllable stress and controllable oil supply under the micro-motion state of the traction sheave, and the abrasion state of the traction sheave is researched.

Description

Technical Field

[0001] The invention relates to the technical field of elevator traction wheel testing, and in particular to a friction testing machine for an elevator traction wheel under micro-motion conditions. Background Art

[0002] The traction sheave is a vital component in the elevator system, which is responsible for transmitting the rotational motion of the motor to the elevator car. In the micro-motion state, the traction sheave is subjected to huge stress and load, so its friction performance is crucial to the safety and normal operation of the elevator system.

[0003] However, existing traction sheave friction test methods have limitations. Traditional methods often focus on testing under static or low-speed conditions and cannot fully evaluate the performance of the traction sheave under micro-motion conditions.

[0004] In order to solve the above problems, it is necessary to develop a friction testing machine and test method specifically for the traction wheel micro-motion state. Summary of the invention

[0005] The object of the present invention is to overcome the deficiencies of the prior art and to provide a friction testing machine and a testing method for an elevator traction wheel under micro-motion conditions.

[0006] The objective of the present invention is achieved through the following technical solutions:

[0007] A friction testing machine for an elevator traction wheel under micro-motion working conditions comprises a workbench, a traction motor and a plurality of steel ropes which can slide on the workbench, wherein the sliding direction of the traction motor is the same as the Y-axis direction; the output shaft of the traction motor is coaxially provided with a traction wheel; the workbench is also provided with a guide wheel rotatably arranged and a tension wheel slidably arranged, the tension wheel, the guide wheel and the traction wheel are spaced from each other, the moving direction of the tension wheel is parallel to the Z-axis direction, the central axis of the tension wheel, the central axis of the guide wheel and the central axis of the traction wheel are parallel to each other and are all parallel to the X-axis direction; a plurality of the steel ropes are wound around the tension wheel, the guide wheel and the traction wheel; the tension wheel is also transmission-connected to a telescopic mechanism which enables the tension wheel to move in the Z-axis direction; the workbench is also provided with a control mechanism for controlling the micro-motion of the traction motor on the workbench along the Y-axis direction.

[0008] Further, in the present invention, the control mechanism includes a dual-output shaft motor disposed on the workbench. The central axes of the two output shafts of the dual-output shaft are collinear and both are parallel to the X-axis direction. Any output shaft of the dual-output shaft motor is coaxially connected with a disc. An arc-shaped groove is formed on the side wall of the disc away from the dual-output shaft motor, and a steering handle is rotatably disposed. The hinge point of the steering handle and the disc is offset from the center of the disc. The center of the arc-shaped groove, the hinge point of the steering handle and the disc are collinear. A bolt adapted to the arc-shaped groove is rotatably disposed at the free end of the steering handle. One end of the bolt is inserted into the arc-shaped groove. The bolt is threadedly connected with a nut, and the nut enables the bolt to stay at any position within the arc-shaped groove. The bolt is hinged with a connecting rod, and the free end of the connecting rod is hinged to one side of the traction motor, and the connection point of the connecting rod and the traction motor is lower than the center of the disc in the YZ plane.

[0009] Further, in the present invention, a sliding plate that can slide along the Z-axis direction is disposed on the workbench, and the tension pulley is rotatably connected to the sliding plate. The telescopic mechanism includes a double-acting cylinder disposed on the workbench, and the piston rod of the double-acting cylinder is connected to the sliding plate. A pressure spring is further disposed at the top end of the piston rod of the double-acting cylinder, and the free end of the pressure spring is connected to the sliding plate.

[0010] Further, in the present invention, a plurality of wheel grooves for accommodating a plurality of the steel wire ropes are formed on the outer peripheral side of the traction wheel, and a heating belt is disposed in any of the wheel grooves.

[0011] Further, in the present invention, an oil supply pipe is disposed on the workbench, and a plurality of oil nozzles are spacedly disposed on the oil supply pipe. A plurality of the oil nozzles are all located above the traction wheel, and a plurality of the oil nozzles correspond to a plurality of the wheel grooves one by one.

[0012] Further, in the present invention, an X-axis guide rail extending along the X-axis direction is disposed on the workbench. The X-axis guide rail is located between the guide wheel and the traction wheel. A movable high-speed camera is slidably disposed on the X-axis guide rail. The moving direction of the high-speed camera is the same as the X-axis direction, and the high-speed camera is used for taking fixed-point photographs of the wheel grooves of the traction wheel.

[0013] Further, in the present invention, a protective cover is disposed on the workbench, and both the guide wheel and the traction wheel are located within the protective cover. A noise detection device is also disposed on the workbench.

[0014] A friction test method for an elevator traction wheel under micro-motion conditions includes the following steps:

[0015] Step 1: Before the test starts, due to the constraint of the self-weight of the tension pulley and the inherent length of the wire rope, the mechanism composed of the traction sheave, the guide pulley, the tension pulley and several wire ropes is in a tensioned state;

[0016] Step 2: After initializing all parameters on the computer center, start the traction motor alone, adjust the speed of the traction motor, and control its forward and reverse rotation, and record various data under the condition of no additional load and no micro-movement;

[0017] Step 3: Start the double-output shaft motor, and the double-output shaft motor controls the traction motor to perform micro-movements with adjustable frequency and degree along the Y-axis direction; among them, the degree of micro-movement is adjusted by the steering handle. Manually turn the steering handle, record the rotation angle of the steering handle, calculate the radius of the "crank", and thus calculate different amplitudes (i.e., vibration amplitudes) of the micro-movement of the traction sheave;

[0018] Step 4: Open the double-acting cylinder, and the computer center accurately controls the bidirectional air intake of the double-acting cylinder. During the operation process, regularly calculate the friction force received by the traction sheave and the equivalent friction coefficient of the traction sheave.

[0019] Further, in Step 3, the calculation method of the vibration amplitude is specifically as follows:

[0020] The calculation formula for the radius r of the "crank" is as follows:

[0021]

[0022] Among them, the radius r of the "crank" is the distance between the central axis of the bolt and the center of the disc in the YZ plane; l is the distance between the fixed point of the steering handle (the hinge point of the steering handle and the disc) and the central axis of the bolt in the YZ plane; e is the distance between the fixed point of the steering handle and the center of the crank (the center of the disc) in the YZ plane; δ is the rotation angle of the steering handle (the angle between the center line of the steering handle and the Y-axis in the YZ plane);

[0023] The "crank" rotation angle β is obtained from the obtained radius r of the "crank":

[0024]

[0025] The horizontal displacement x of the connecting rod is obtained through the limit state and geometric relationship of the connecting rod:

[0026]

[0027] Among them: β(t) = β + vt,

[0028] When the steering handle is turned to 0° (i.e., the angle between the steering handle and the Y-axis is 0°), at this time the radius of the "crank" is 0, and the traction sheave is not affected by micro-movement. Let the position of the traction sheave at this time be the zero point, then the position of the connecting rod:

[0029]

[0030] Then the slight movement degree of the traction wheel is:

[0031]

[0032] Wherein, v is the rotational speed of the disc; t is the running time of the test machine after adjusting the steering handle; L is the length of the connecting rod; β is the crank angle (the angle between two connecting lines in the YZ plane, the two connecting lines are respectively: the connecting line between the central axis of the bolt and the center of the disc; the connecting line between the fixed point of the steering handle and the center of the disc); C is the swing angle of the connecting rod (the angle between the center line of the connecting rod and the Y-axis in the YZ plane); E is the eccentricity of the connecting rod (the distance between the projection points of the center of the disc, the connection point of the connecting rod and the traction motor on the Z-axis in the YZ plane).

[0033] Further, in step 4, the friction force F received by the traction wheel f and the calculation method of the equivalent friction coefficient f of the traction wheel are specifically as follows:

[0034] The external force F applied by the double-acting cylinder:

[0035]

[0036] The friction force F received by the traction wheel f :

[0037]

[0038] The equivalent friction coefficient f of the traction wheel:

[0039]

[0040] Wherein, the pressures input into the rodless cavity and the rod cavity of the double-acting cylinder through the air pipe are P1 and P2 respectively; the diameter of the piston rod is d; the inner diameter of the piston rod cylinder is D; ΔF is the pressure difference of the steel wire ropes at both ends of the traction wheel; F ， is the self-weight of the tensioning wheel and other external forces; A and B are the angles between the two sides of the tensioning wheel and the steel wire rope respectively; α is the wrap angle of the traction wheel.

[0041] The beneficial effects of the present invention are:

[0042] The present invention provides a friction test machine for an elevator traction wheel under a slight movement working condition, which can control the stress state of the traction wheel during the test by simulating the test and combining controllable temperature, controllable force, and controllable oil supply in the slight movement state of the traction wheel, and study its wear state. Description of the Drawings

[0043] Figure 1Schematic diagram of the structure of an embodiment of the present invention;

[0044] Figure 2 Schematic diagram of the structure of an embodiment of the present invention;

[0045] Figure 3 Schematic diagram of the structure of an embodiment of the present invention;

[0046] Figure 4 Schematic diagram of the structure of an embodiment of the present invention;

[0047] Figure 5 is Figure 2 left view of;

[0048] Figure 6 is Figure 2 rear view of;

[0049] Figure 7 is Figure 4 partial enlarged view at position A in;

[0050] Figure 8 Schematic diagram of the structure of the double-acting cylinder of an embodiment of the present invention;

[0051] Figure 9 Schematic diagram of the structure of the wire rope in a tensioned state of an embodiment of the present invention;

[0052] Figure 10 Schematic diagram of the structure of the control mechanism of an embodiment of the present invention;

[0053] Figure 11 Schematic diagram of the installation structure of the steering handle of an embodiment of the present invention.

[0054] In the figure: 1 - workbench; 2 - traction motor; 3 - wire rope; 4 - traction wheel; 5 - guide wheel; 6 - tensioning wheel; 701 - double-output shaft motor; 702 - disc; 703 - arc groove; 704 - steering handle; 705 - bolt; 706 - nut; 707 - connecting rod; 8 - sliding plate; 9 - double-acting cylinder; 901 - piston rod; 902 - rod chamber; 903 - rodless chamber; 10 - heating tape; 1101 - oil supply pipe; 1102 - oil nozzle; 1201 - X-axis guide rail; 1202 - high-speed camera; 1301 - protective cover; 1302 - noise detection device. Detailed implementation manners

[0055] Next, the technical solutions of the present invention will be clearly and completely described in conjunction with the embodiments. 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 skilled in the art based on the embodiments of the present invention without creative efforts fall within the scope of protection of the present invention.

[0056] See also Figures 1-11 , the present invention provides a technical solution:

[0057] A friction tester for an elevator traction wheel under micro-motion conditions comprises a workbench 1, a traction motor 2 which can slide on the workbench 1, and a plurality of steel ropes 3. A Y-axis guide rail (not marked in the figure) is installed on the workbench 1, and the extension direction of the Y-axis guide rail is parallel to the Y-axis direction. The traction motor 2 is installed on the Y-axis guide rail, and its sliding direction is the same as the Y-axis direction. A traction wheel 4 is coaxially mounted on the output shaft of the traction motor 2. A guide wheel 5 is rotatably mounted on the workbench 1, and a tension wheel 6 is slidably mounted on the workbench 1. The tension wheel 6, the guide wheel 5 and the traction wheel 4 are spaced apart from each other. The moving direction of the tension wheel 6 is parallel to the Z-axis direction. The central axis of the tension wheel 6, the central axis of the guide wheel 5 and the central axis of the traction wheel 4 are parallel to each other and are all parallel to the X-axis direction. The outer peripheral side of the traction wheel 4, the outer peripheral side of the guide wheel 5 and the outer peripheral side of the tension wheel 6 are all provided with a plurality of wheel grooves for accommodating a plurality of steel wire ropes 3. A plurality of steel wire ropes 3 are wound around the tension wheel 6, the guide wheel 5 and the traction wheel 4 (i.e., they are wound one by one in the corresponding wheel grooves). The tension wheel 6 is also transmission-connected to a telescopic mechanism that enables it to move in the Z-axis direction. A control mechanism for controlling the traction motor 2 to fine-move along the Y-axis direction on the Y-axis guide rail is also mounted on the workbench 1.

[0058] Specifically, the control mechanism in this embodiment includes a dual-output shaft motor 701 installed on the workbench 1, the central axes of the two output shafts of the dual-output shaft are collinear and parallel to the X-axis direction; any output shaft of the dual-output shaft motor 701 is coaxially connected with a disk 702, and the side wall of the disk 702 away from the dual-output shaft motor 701 is provided with an arc groove 703 and a steering handle 704 is rotatably installed, the hinge point of the steering handle 704 and the disk 702 and the center of the disk 702 are staggered, and the center of the arc groove 703 and the hinge point of the steering handle 704 and the disk 702 are collinear. The free end of the steering handle 704 is rotatably installed with a bolt 705 adapted to the arc groove 703, one end of the bolt 705 is inserted into the arc groove 703, and the bolt 705 is threadedly connected with a nut 706, and the nut 706 enables the bolt 705 to stay at any position in the arc groove 703. In this embodiment, the adjustment range of the steering handle 704 is 0-60°, and the step unit is 1°. Figure 11 When the angle of the steering handle 704 needs to be adjusted, the nut 706 is screwed to separate one side of the nut 706 from one side of the disc 702. At this time, the steering handle 704 can be rotated. When the steering handle 704 is adjusted to a suitable angle, the nut 706 is screwed to make one side of the nut 706 abut against one side of the disc 702. The squeezing force between the nut 706 and the disc 702 prevents the bolt 705 from moving in the arc groove 703. At this time, the steering handle 704 cannot swing around the hinge point between itself and the disc 702.

[0059] The bolt 705 is hinged with a connecting rod 707. The free end of the connecting rod 707 is hinged to one side of the traction motor 2, and the connection point of the connecting rod 707 and the traction motor 2 is lower than the center of the disc 702 in the YZ plane.

[0060] In this way, the double-output shaft motor 701 controls the traction motor 2 to be in a micro-motion state with variable degree and frequency on the Y-axis guide rail through the steering handle 704 and the connecting rod 707. The micro-motion degree is adjusted by the steering handle 704, and the frequency is controlled by the double-output shaft motor 701, and then the micro-motion of the traction wheel 4 is formed through the output shaft of the traction motor 2.

[0061] In this embodiment, in order to facilitate the installation of the tensioning wheel 6, as Figure 3 shown, a slide plate 8 that can slide in the Z-axis direction is installed on the workbench 1, and the tensioning wheel 6 is rotatably connected to the slide plate 8. In this embodiment, the telescopic mechanism selects a double-acting cylinder 9. The double-acting cylinder 9 is installed on the workbench 1, and its installation method needs to make the central axis of its piston rod 901 parallel to the Z-axis direction. The piston rod 901 of the double-acting cylinder 9 is connected to the slide plate 8. The telescopic movement of the piston rod 901 in the Z-axis direction can control the position of the tensioning wheel 6.

[0062] In addition, in this embodiment, a pressure spring (not shown in the figure) is further installed at the top end of the piston rod 901 of the double-acting cylinder 9, and the free end of the pressure spring is connected to the slide plate 8. Installing the pressure spring here helps to reduce the vibration of the tensioning wheel 6 and the entire testing machine during tensioning, ensuring that the micro-motion of the traction wheel 4 is only provided by the control mechanism.

[0063] Referring to Figure 5 , in this embodiment, a heating belt 10 is installed in each groove of the traction wheel 4, which can ensure that each groove is heated evenly.

[0064] Referring to Figure 2 , Figure 4 and Figure 5 , in this embodiment, an oil supply pipe 1101 is further installed on the workbench 1. A number of oil nozzles 1102 are arranged at intervals on the oil supply pipe 1101. A number of oil nozzles 1102 are all located above the traction wheel 4, and a number of oil nozzles 1102 correspond to a number of grooves one by one. The oil supply pipe 1101 is communicated with a supporting oil supply device. When oil supply is required, the lubricating oil in the oil supply pipe 1101 can be dripped into each groove of the traction wheel 4 through each oil nozzle 1102 to ensure sufficient oil supply when the traction wheel 4 is working, and a number of oil nozzles 1102 can drip separately and selectively at the groove of each traction wheel 4 to compare the influence of oil supply conditions.

[0065] In this embodiment, an X-axis guide rail 1201 extending in the X-axis direction is provided on the workbench 1. The X-axis guide rail 1201 is located between the guide wheel 5 and the traction wheel 4. A movable high-speed camera 1202 is slidably arranged on the X-axis guide rail 1201. The moving direction of the high-speed camera 1202 is the same as the X-axis direction. The high-speed camera 1202 is used to perform fixed-point shooting on the wheel groove of the traction wheel 4 after the experiment to extract the wear condition of the working surface of the wheel groove.

[0066] In this embodiment, a protective cover 1301 is installed on the workbench 1. Both the guide wheel 5 and the traction wheel 4 are located inside the protective cover 1301; a noise detection device 1302 is also installed on the workbench 1.

[0067] After the tester finishes the steps required for the test, the noise detection device 1302 is turned on. At this time, the laboratory needs to be kept relatively quiet to ensure the normal operation of the noise detection device 1302. After the experiment is over, the noise detection device 1302 is turned off. The noise detection device 1302 transmits the received sound back to the industrial control computer to monitor the noise situation. When the traction wheel 4 runs to the set working cycle, the traction motor 2 stops working. After each test interval ends, 5 minutes should be maintained to stabilize the system state.

[0068] A friction test method for an elevator traction wheel 4 under a micro-motion condition includes the following steps:

[0069] Step 1: Before the test starts, the mechanism composed of the traction wheel 4, the guide wheel 5, the tensioning wheel 6, and several steel wires 3 is put into a tensioned state by the constraint of the self-gravity of the tensioning wheel 6 and the inherent length of the steel wire rope 3;

[0070] Step 2: After initializing all parameters on the computer center, start the traction motor 2 alone, adjust the rotation speed of the traction motor 2, and control its forward and reverse rotation, and record various data under the condition of no additional load and no micro-motion state;

[0071] Step 3: Start the double-output shaft motor 701. The double-output shaft motor 701 controls the traction motor 2 to perform micro-motion with adjustable frequency and degree along the Y-axis direction; among them, the micro-motion degree is adjusted by the steering handle 704. Manually turn the steering handle 704, record the rotation angle of the steering handle 704, calculate the radius of the "crank", and thus calculate different amplitudes (i.e., vibration amplitudes) of the micro-motion of the traction wheel 4;

[0072] Step 4: Open the double-acting cylinder 9. The computer center precisely controls the bidirectional air intake of the double-acting cylinder 9, and regularly calculates the friction force received by the traction wheel 4 and the equivalent friction coefficient of the traction wheel 4 during the operation process.

[0073] Further, in Step 3, the calculation method of the vibration amplitude is specifically as follows:

[0074] The calculation formula for the radius r of the "crank" is as follows:

[0075]

[0076] Among them, the radius r of the "crank" is the distance between the central axis of the bolt 705 and the center of the disk 702 in the YZ plane; l is the distance between the fixed point of the steering handle 704 (the hinge point of the steering handle and the disk) and the central axis of the bolt 705 in the YZ plane; e is the distance between the fixed point of the steering handle 704 and the crank center (the center of the disk) in the YZ plane; δ is the rotation angle of the steering handle 704 (the angle between the center line of the steering handle and the Y axis in the YZ plane).

[0077] The "crank" rotation angle β is obtained from the calculated "crank" radius r:

[0078]

[0079] The horizontal displacement x of the connecting rod 707 is obtained through the limit state and geometric relationship of the connecting rod 707:

[0080]

[0081] Among them: β(t) = β + vt,

[0082] When the steering handle 704 is turned to 0° (i.e., the angle between the steering handle and the Y axis is 0°), at this time the "crank" radius is 0, and the traction wheel 4 is not affected by the micro-movement. Assuming the position of the traction wheel 4 at this time is the zero point, then the position of the connecting rod 707:

[0083]

[0084] Then the degree of micro-movement of the traction wheel 4:

[0085]

[0086] Among them, v is the rotational speed of the disk 702; t is the running time of the test machine after the steering handle 704 is adjusted; L is the length of the connecting rod 707; β is the crank rotation angle (the angle between two connecting lines in the YZ plane, the two connecting lines are respectively: the connecting line between the central axis of the bolt and the center of the disk; the connecting line between the fixed point of the steering handle and the center of the disk); C is the swing angle of the connecting rod 707 (the angle between the center line of the connecting rod and the Y axis in the YZ plane); E is the eccentricity of the connecting rod 707 (the distance between the projection points of the center of the disk, the connection point of the connecting rod and the traction motor on the Z axis in the YZ plane).

[0087] Furthermore, in step 4, the friction force F f received by the traction wheel 4 and the calculation method of the equivalent friction coefficient f of the traction wheel 4 are specifically as follows:

[0088] The external force F applied by the double-acting cylinder 9:

[0089]

[0090] The frictional force F on the traction wheel 4 f :

[0091]

[0092] The equivalent friction coefficient f of the traction wheel 4:

[0093]

[0094] Among them, the pressures input through the air pipes in the rodless chamber 903 and the rod chamber 902 of the double-acting cylinder 9 are P1 and P2 respectively; d is the diameter of the piston rod 901; D is the inner diameter of the cylinder of the piston rod 901; ΔF is the pressure difference between the wire ropes 3 at both ends of the traction wheel 4; F ， is the self-weight of the tensioning wheel 6 and other external forces; A and B are the angles between the two sides of the tensioning wheel 6 and the wire rope 3 respectively; α is the wrap angle of the traction wheel 4 (referring to the included angle between the traction wheel and the wire rope).

[0095] Working principle:

[0096] Before the test starts, the entire device is in a tensioned state through the constraint of the self - gravity of the tension pulley 6 and the inherent length of the traction steel wire rope 3. After initializing all parameters on the industrial control computer, start the traction motor 2 alone, input the required rotational speed for the test, control the forward and reverse rotation, and turn the steering handle 704 to the position where the angle between the steering handle 704 and the Y - axis is 0° (i.e., 0°). Record various data under the condition of no additional load and no micro - movement, and calculate the position of the connecting rod 707 at this time. Continue to turn the steering handle 704, record the turned angle, calculate the radius of the "crank" and the rotation angle of the steering handle 704 according to the formula, and input the rotation angle of the steering handle 704 on the industrial control computer. Start the double - output - shaft motor 701, and calculate the horizontal displacement and micro - movement degree of the connecting rod 707. Select to turn on the oil supply device and the heating tape 10 according to the test requirements. After starting the heating tape 10, pay attention to observing the difference between the real - time temperature and the set temperature. Open the double - acting cylinder 9, input the two - way air intake on the industrial control computer, and regularly calculate the friction force and the equivalent friction coefficient during the operation. When the tester has completed all the steps required for the test, turn on the noise detection device 1302. At this time, the laboratory needs to be relatively quiet to ensure the normal operation of the noise detection device 1302. After the experiment is over, first turn off the noise detection device 1302. When the traction wheel 4 runs to the set working cycle, stop the traction motor 2. After each test interval ends, keep it for 5 minutes to stabilize the system state. Then make the high - speed camera 1202 enter the inside of the protective cover 1301 along the X - axis guide rail 1201 to take fixed - point pictures of the grooves of the traction wheel 4. Finally, use the industrial control computer to analyze the taken pictures, extract the wear condition of the working surface of the grooves, generate the friction coefficient and wear morphology diagrams, and combine with the sound fluctuation curve diagram to explore the test results.

[0097] The above - mentioned is only the preferred embodiment of the present invention. It should be understood that the present invention is not limited to the form disclosed herein, should not be regarded as excluding other embodiments, but can be used in various other combinations, modifications and environments, and can be changed within the scope of the concept described herein through the above teachings or the technology or knowledge in related fields. And any changes and modifications made by those skilled in the art without departing from the spirit and scope of the present invention should fall within the protection scope of the appended claims of the present invention.

Claims

1. A friction tester for an elevator traction sheave under micro-motion conditions, characterized in that: The invention comprises a workbench (1), a traction motor (2) which can slide on the workbench (1), and a plurality of steel wire ropes (3), wherein the sliding direction of the traction motor (2) is the same as the Y-axis direction; a traction wheel (4) is coaxially arranged on the output shaft of the traction motor (2); a guide wheel (5) is rotatably arranged on the workbench (1) and a tension wheel (6) is slidably arranged on the workbench (1), wherein the tension wheel (6), the guide wheel (5) and the traction wheel (4) are spaced from each other, and the moving direction of the tension wheel (6) is parallel to the Z-axis direction. The central axis of the tension wheel (6), the central axis of the guide wheel (5) and the central axis of the traction wheel (4) are parallel to each other and are all parallel to the X-axis direction; a plurality of the steel wire ropes (3) are wound around the tension wheel (6), the guide wheel (5) and the traction wheel (4); the tension wheel (6) is also connected to a telescopic mechanism for moving the tension wheel in the Z-axis direction; and the workbench (1) is also provided with a control mechanism for controlling the traction motor (2) to move slightly along the Y-axis direction on the workbench (1).

2. The friction testing machine for an elevator traction sheave under micro-motion conditions according to claim 1, characterized in that: The control mechanism comprises a dual-output shaft motor (701) arranged on the workbench (1), the central axes of the two output shafts of the dual-output shafts are collinear and parallel to the X-axis direction; any output shaft of the dual-output shaft motor (701) is coaxially connected to a disk (702), the side wall of the disk (702) away from the dual-output shaft motor (701) is provided with an arc-shaped groove (703) and a steering handle (704) for rotation, the hinge point of the steering handle (704) and the disk (702) and the center of the disk (702) are staggered, and the center of the arc-shaped groove (703) and the hinge point of the steering handle (704) and the disk (702) are collinear. The free end of the steering handle (704) is rotatably provided with a bolt (705) adapted to the arc-shaped groove (703), one end of the bolt (705) is inserted into the arc-shaped groove (703), and the bolt (705) is threadedly connected with a nut (706), and the nut (706) enables the bolt (705) to stay at any position in the arc-shaped groove (703); the bolt (705) is hinged with a connecting rod (707), the free end of the connecting rod (707) is hinged with one side of the traction motor (2), and the connection point between the connecting rod (707) and the traction motor (2) is lower than the center of the disc (702) on the YZ plane.

3. The friction testing machine for an elevator traction sheave under micro-motion conditions according to claim 1, characterized in that: The workbench (1) is provided with a slide plate (8) which can slide along the Z-axis direction, and the tensioning wheel (6) is rotatably connected to the slide plate (8); the telescopic mechanism comprises a double-acting cylinder (9) arranged on the workbench (1), and the piston rod (901) of the double-acting cylinder (9) is connected to the slide plate (8); the top end of the piston rod (901) of the double-acting cylinder (9) is also provided with a pressure spring, and the free end of the pressure spring is connected to the slide plate (8).

4. The friction testing machine for an elevator traction sheave under micro-motion conditions according to claim 1, characterized in that: A plurality of wheel grooves for accommodating a plurality of the steel wire ropes (3) are provided on the outer peripheral side of the traction wheel (4), and a heating belt (10) is provided in any of the wheel grooves.

5. The friction testing machine for an elevator traction sheave under micro-motion conditions according to claim 4, characterized in that: The workbench (1) is provided with an oil supply pipe (1101), and a plurality of oil nozzles (1102) are arranged at intervals on the oil supply pipe (1101). The plurality of oil nozzles (1102) are all located above the traction wheel (4), and the plurality of oil nozzles (1102) correspond one-to-one to the plurality of wheel grooves.

6. The friction testing machine for an elevator traction sheave under micro-motion conditions according to claim 1, characterized in that: The workbench (1) is provided with an X-axis guide rail (1201) extending along the X-axis direction, the X-axis guide rail (1201) is located between the guide wheel (5) and the traction wheel (4), and a movable high-speed camera (1202) is slidably provided on the X-axis guide rail (1201), the moving direction of the high-speed camera (1202) is the same as the X-axis direction, and the high-speed camera (1202) is used to take fixed-point photographs of the wheel groove of the traction wheel (4).

7. The friction testing machine for an elevator traction sheave under micro-motion conditions according to claim 1, characterized in that: The workbench (1) is provided with a protective cover (1301), and the guide wheel (5) and the traction wheel (4) are both located inside the protective cover (1301); the workbench (1) is also provided with a noise detection device (1302).

8. A friction test method for an elevator traction sheave under micro-motion conditions, characterized in that: A friction tester for an elevator traction sheave (4) under micro-motion conditions using the friction tester according to any one of claims 1 to 7 comprises the following steps: Step 1: Before the test begins, the mechanism consisting of the traction wheel (4), the guide wheel (5), the tension wheel (6) and the plurality of steel ropes (3) is in a tensioned state by the self-weight of the tension wheel (6) and the restraining effect of the inherent length of the steel rope (3); Step 2: After initializing all parameters on the computer center, start the traction motor (2) separately, adjust the speed of the traction motor (2), and control its forward and reverse rotation, and record various data in a state without additional load and without micro-motion; Step 3, starting the dual output shaft motor (701), the dual output shaft motor (701) controls the traction motor (2) to perform frequency and degree adjustable micro-motion along the Y-axis direction; wherein the micro-motion degree is adjusted by the steering handle (704), the steering handle (704) is manually turned, the steering handle (704) angle is recorded, and the "crank" radius is calculated, thereby calculating the different amplitudes (i.e. vibration amplitudes) of the micro-motion of the traction wheel (4); Step 4, open the double-acting cylinder (9), the computer center accurately controls the bidirectional air intake of the double-acting cylinder (9), and regularly calculates the friction force on the traction wheel (4) and the equivalent friction coefficient of the traction wheel (4) during operation.

9. A friction test method for an elevator traction sheave under micro-motion conditions according to claim 8, characterized in that: In step 3, the vibration amplitude is calculated as follows: The calculation formula of the "crank" radius r is as follows: Wherein, the radius of the "crank" r is the distance between the center axis of the bolt (705) and the center of the disk (702) on the YZ plane; l is the distance between the fixed point of the steering handle (704) (the hinge point between the steering handle and the disk) and the center axis of the bolt (705) on the YZ plane; e is the distance between the fixed point of the steering handle (704) and the center of the crank (the center of the disk) on the YZ plane; δ is the rotation angle of the steering handle (704) (the angle between the center line of the steering handle and the Y axis on the YZ plane); The crank angle β is obtained from the obtained crank radius r: The horizontal displacement x of the connecting rod (707) is obtained by the limit state and geometric relationship of the connecting rod (707): Where: β(t)=β+vt, When the steering handle (704) is turned to 0° (i.e., the angle between the steering handle and the Y axis is 0°), the radius of the "crank" is 0, and the traction wheel (4) is not affected by the micro-motion. Assuming that the position of the traction wheel (4) at this time is the zero point, the position of the connecting rod (707) is: Then the micro-motion degree of the traction sheave (4) is: Wherein, v is the rotation speed of the disc (702); t is the running time of the test machine after the steering handle (704) is adjusted; L is the length of the connecting rod (707); β is the crank angle (the angle between two connecting lines on the YZ plane, the two connecting lines are: the connecting line between the central axis of the bolt and the center of the disc; the connecting line between the fixed point of the steering handle and the center of the disc); C is the swing angle of the connecting rod (707) (the angle between the center line of the connecting rod and the Y axis on the YZ plane); E is the eccentricity of the connecting rod (707) (the distance between the projection points of the center of the disc and the connection point of the connecting rod and the traction motor on the Z axis on the YZ plane).

10. A friction test method for an elevator traction sheave under micro-motion conditions according to claim 8, characterized in that: In step 4, the friction force F on the traction sheave (4) is f The calculation method of the equivalent friction coefficient f of the traction sheave (4) is as follows: External force F applied by double-acting cylinder (9): The friction force F on the traction sheave (4) f : Equivalent friction coefficient f of the traction sheave (4): The pressures inputted into the rodless chamber (903) and the rod chamber (902) in the double-acting cylinder (9) through the air pipe are P1 and P2 respectively; d is the diameter of the piston rod (901); D is the inner diameter of the straight cylinder of the piston rod (901); ΔF is the pressure difference of the steel wire rope (3) at both ends of the traction wheel (4); F ， The tension wheel (6) has its own gravity and other external forces; A and B are the angles between the two sides of the tensioning wheel (6) and the steel wire rope (3) respectively; α is the wrap angle of the traction wheel (4).

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