Belt-type dynamometer with deviation rectifying function

Abstract

The application discloses a belt-type dynamometer with a deviation rectifying function and belongs to the technical field of belt-type dynamometers, and the technical scheme is as follows: a rack, driving hub bearing seats arranged on both sides of one end of the rack, driven hub bearing seats slidably arranged on the rack, driving hubs rotatably arranged on the two driving hub bearing seats, driven hubs rotatably arranged on the two driven hub bearing seats, and a steel belt for transmission between the driving hubs and the driven hubs; the deviation rectifying system further comprises a monitoring device for detecting the deviation of the steel belt, a controller for receiving the deviation signal of the monitoring device and sending a control instruction to a deviation rectifying actuating mechanism based on the deviation signal, and the deviation rectifying actuating mechanism is used for rectifying the deviation of the steel belt according to the control instruction. The application has the beneficial effect that the differential hydraulic circuit is matched with the proportional pressure reducing valve, so that the deviation of the steel belt can be rectified by adjusting the output proportion of the proportional pressure reducing valve while the steel belt is kept in the state of the basic pre-tightening force.

Description

Technical Field

[0001] This invention belongs to the technical field of belt dynamometers, and specifically relates to a belt dynamometer with a correction function. Background Technology

[0002] Belt dynamometers are key equipment used in the automotive R&D and validation phases to test tire, suspension, and overall vehicle dynamics performance. Their core principle lies in using a high-speed running steel belt to simulate a real road surface, pressing the tires of the test vehicle firmly against the belt surface, thereby accurately measuring key parameters such as driving force, braking performance, rolling resistance, and ride comfort. With the rapid development of the automotive industry, especially in the fields of electric and high-performance vehicles, unprecedented demands have been placed on the accuracy, reliability, and extreme capabilities of testing equipment. Modern belt dynamometers can achieve steel belt linear speeds exceeding 50 m / s to meet the testing needs of high-performance vehicles and extreme operating conditions.

[0003] However, at such extremely high operating speeds, the stable operation of the steel belt faces severe challenges. As a flexible, ring-shaped moving component, even slight manufacturing tolerances, installation errors, uneven stress, or thermal expansion of the steel belt are easily amplified during high-speed dynamic processes, leading to lateral slippage or periodic deviation. If left uncontrolled, this lateral deviation can seriously affect the accuracy and repeatability of test data. Severe deviation can even cause the steel belt to scrape and wear against the frame, or even detach from the hub, resulting in serious equipment damage or even personnel safety accidents.

[0004] Therefore, how to achieve active belt alignment of the steel belt at high speeds and ensure its stable center position during long-term operation is a technical challenge in the design of belt dynamometers. Traditional alignment methods generally involve periodic manual adjustments, but these are no longer sufficient to meet the demands of modern high-precision, high-load, and automated testing. Summary of the Invention

[0005] The purpose of this invention is to provide a belt dynamometer with a correction function.

[0006] The present invention is achieved through the following measures: a belt dynamometer with a correction function, characterized in that it includes a frame, active hub bearing seats disposed on both sides of one end of the frame, driven hub bearing seats slidably disposed on the frame, an active hub rotatably disposed on the two active hub bearing seats, a driven hub rotatably disposed on the two driven hub bearing seats, and a steel belt for transmission between the active hub and the driven hub. It also includes a correction system, which includes a monitoring device for detecting the offset of the steel strip and a controller for receiving the offset signal from the monitoring device and sending control commands to the correction actuator based on the offset signal. The correction actuator is used to correct the deviation of the steel strip according to the control command.

[0007] Furthermore, the monitoring device includes four displacement sensors, and laser displacement sensors can be selected. Two displacement sensors are used to monitor the displacement of the steel belt on the driving hub, and two other displacement sensors are used to monitor the displacement of the steel belt on the driven hub.

[0008] Furthermore, it also includes a hydraulic system for driving the correction actuator; The hydraulic system includes a first cylinder and a second cylinder symmetrically arranged on the frame for driving the driven hub bearing seat to move, and hydraulic circuits for controlling the first cylinder and the second cylinder respectively. Both hydraulic circuits include a solenoid valve assembly for reversing and maintaining pressure, and a proportional pressure reducing valve connected to the rod chamber for pressure control.

[0009] Furthermore, the solenoid valve assembly includes a three-position four-way directional valve with a neutral position function; The three-position four-way directional valve has its B port connected to the inlet of the proportional pressure reducing valve, its A port connected to the rodless chamber of the oil cylinder, its P port connected to the oil pump, and its T port connected to the oil tank. The oil outlet of the proportional pressure reducing valve is connected to the rod chamber of the oil cylinder and the oil inlet of the speed control valve, respectively. The oil outlet of the speed control valve and the oil inlet of the oil pump are both connected to the oil tank. The P ports of the two three-position four-way directional valves are connected, and the T ports of the two three-position four-way directional valves are connected. The oil outlets of the two speed control valves are connected; A check valve is installed between the oil outlet of the oil pump and the two P oil ports. A bypass is provided between the oil pump outlet and the oil tank, and an overflow valve is connected to the bypass. When the three-position four-way directional valve is in the neutral position, ports A, B, and P are connected, while port T is closed.

[0010] This embodiment provides another form of solenoid valve assembly, wherein the solenoid valve assembly includes one two-position four-way directional valve, one normally closed two-position two-way solenoid valve, and one normally open two-position two-way solenoid valve. The two-position four-way directional valve has its B port connected to the inlet of the proportional pressure reducing valve, its A port connected to the rodless chamber of the oil cylinder, its P port connected to the oil pump, and its T port connected to the oil tank. The oil outlet of the proportional pressure reducing valve is connected to the rod chamber of the oil cylinder and the oil inlet of the speed control valve, respectively. A normally closed two-position two-way solenoid valve is installed between port B and the inlet of the proportional pressure reducing valve, and a normally open two-position two-way solenoid valve is installed between port A and the inlet of the proportional pressure reducing valve. The oil outlet of the speed control valve and the oil inlet of the oil pump are connected to the oil tank. The P ports of the two two-position four-way directional valves are connected, and the T ports of the two two-position four-way directional valves are connected. The oil outlets of the two speed control valves are connected; A check valve is provided between the oil outlet of the oil pump and the two P oil ports. The check valve is used to prevent the system pressure oil from flowing back to the pump and to protect the pump when it is stopped or unloaded. A bypass is provided between the oil pump outlet and the oil tank, and an overflow valve is connected to the bypass. The overflow valve serves as overpressure protection, allowing excess flow to overflow back into the oil tank.

[0011] Furthermore, the oil outlet of the one-way valve is connected to an accumulator.

[0012] Furthermore, a force sensor is installed between the push rod of the hydraulic cylinder and the driven hub bearing housing, and the thrust of the hydraulic cylinder can be collected in real time through the force sensor.

[0013] Furthermore, the frame is provided with guide holes, and the driven hub bearing seat is provided with guide posts corresponding to the guide holes. The inner diameter of the guide holes is slightly larger than the outer diameter of the guide posts.

[0014] Specifically, in the above scheme, the speed control valve can enable the proportional pressure reducing valve to meet its usage requirements, while the speed control valve can ensure that the flow rate is the same under different pressures.

[0015] Furthermore, a pressure gauge is generally installed on the main circuit of the hydraulic circuit to monitor the pressure of the main circuit, so as to ensure the normal operation of the circuit.

[0016] The beneficial effects of the technical solution provided by the embodiments of the present invention are as follows: This application adopts a differential hydraulic circuit combined with a proportional pressure reducing valve design, so that the steel strip can be corrected by adjusting the output ratio of the proportional pressure reducing valve while maintaining the basic preload. In addition, since the proportional pressure reducing valve is in the maximum output state when the steel strip is in working condition, during the correction process, only the output of the proportional pressure reducing valve needs to be reduced to change the output thrust of the hydraulic cylinder, thereby achieving steel strip correction. The proportional pressure reducing valve operates from the maximum output state, avoiding the poor control range of low response speed and high overshoot, and trying to meet the need for correction at high speed. Attached Figure Description

[0017] To more clearly illustrate the technical solution of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. Obviously, the drawings listed below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the overall structure in an embodiment of the present invention; Figure 2 This is in the embodiments of the present invention and Figure 1 Schematic diagrams of structures at different angles; Figure 3 It is the hydraulic circuit of the correction actuator. Figure 1 ; Figure 4 It is the hydraulic circuit of the correction actuator. Figure 2 .

[0019] The components represented by each number in the attached diagram are listed below: 1. Driven hub; 2. Driven hub; 3. Steel belt; 4. Frame; 5. Motor; 7. Displacement sensor; 8. Force sensor; 9. Guide post; 10. Guide hole; 101. Driven hub bearing housing; 201. Driven hub bearing housing; 311. First hydraulic cylinder; 312. Second hydraulic cylinder; 313. Speed ​​control valve one; 314. Speed ​​control valve two; 315. Proportional pressure reducing valve one; 316. 317. Proportional pressure reducing valve II; 318. Three-position four-way directional valve I; 319. Three-position four-way directional valve II; 320. Relief valve; 321. Oil pump; 322. Accumulator; 323. Normally open two-position two-way solenoid valve I; 324. Normally closed two-position two-way solenoid valve I; 325. Normally closed two-position two-way solenoid valve II; 326. Two-position four-way directional valve I; 327. Two-position four-way directional valve II. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to embodiments. Of course, the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0021] Example 1: See Figures 1-3 A belt dynamometer with a correction function is characterized by comprising a frame 4, active hub bearing seats 101 disposed on both sides of one end of the frame 4, driven hub bearing seats 201 slidably disposed on the frame 4, an active hub 1 rotatably disposed on the two active hub bearing seats 101, a driven hub 2 rotatably disposed on the two driven hub bearing seats 201, and a steel belt 3 for transmission between the active hub 1 and the driven hub 2; the active hub 1 is driven by a motor 5, which is disposed on the frame 4; It also includes a correction system, which includes a monitoring device for detecting the offset of the steel strip 3, and a controller for receiving the offset signal from the monitoring device and sending control commands to the correction actuator based on the offset signal. The correction actuator is used to correct the deviation of the steel strip 3 according to the control command.

[0022] The monitoring device includes four displacement sensors 7, and laser displacement sensors can be selected. Two displacement sensors 7 are used to monitor the displacement of the steel belt 3 on the driving hub 1, and two other displacement sensors 7 are used to monitor the displacement of the steel belt 3 on the driven hub 2.

[0023] It also includes the hydraulic system that drives the correction actuator; The hydraulic system includes a first cylinder 311 and a second cylinder 312 symmetrically arranged on the frame 4 for driving the driven hub bearing seat 201 to move, and hydraulic oil circuits for controlling the first cylinder 311 and the second cylinder 312 respectively. Both hydraulic circuits include a solenoid valve assembly for reversing and maintaining pressure, and a proportional pressure reducing valve connected to the rod chamber for pressure control.

[0024] The solenoid valve assembly includes a three-position four-way directional valve with a neutral position function; The B port of the three-position four-way directional valve is connected to the inlet of the proportional pressure reducing valve, the A port is connected to the rodless chamber of the oil cylinder, the P port is connected to the oil pump 320, and the T port is connected to the oil tank. The oil outlet of the proportional pressure reducing valve is connected to the rod chamber of the oil cylinder and the oil inlet of the speed control valve, respectively. The oil outlet of the speed control valve and the oil inlet of the oil pump 320 are both connected to the oil tank; The P ports of the two three-position four-way directional valves are connected, and the T ports of the two three-position four-way directional valves are connected. The oil outlets of the two speed control valves are connected; A check valve is installed between the oil outlet of oil pump 320 and the two P oil ports; A bypass is provided between the oil outlet of the oil pump 320 and the oil tank, and an overflow valve 319 is connected to the bypass. When the three-position four-way directional valve is in the neutral position, ports A, B, and P are connected, while port T is closed.

[0025] like Figure 3 As shown, specifically, the B port of the three-position four-way directional valve 317 is connected to the inlet of the proportional pressure reducing valve 315, the A port is connected to the rodless chamber of the first cylinder 311, the P port is connected to the oil pump 320, and the T port is connected to the oil tank. The oil outlet of the proportional pressure reducing valve 315 is connected to the rod chamber of the first oil cylinder 311 and the oil inlet of the speed regulating valve 313, respectively. The oil outlet of speed control valve 313 and the oil inlet of oil pump 320 are both connected to the oil tank; The B port of the three-position four-way directional valve 318 is connected to the inlet of the proportional pressure reducing valve 316, the A port is connected to the rodless chamber of the second cylinder 312, the P port is connected to the oil pump 320, and the T port is connected to the oil tank. The oil outlet of the proportional pressure reducing valve 316 is connected to the rod chamber of the second oil cylinder 312 and the oil inlet of the speed regulating valve 314, respectively. The oil outlet of speed control valve 314 and the oil inlet of oil pump 320 are both connected to the oil tank; The P ports of the three-position four-way directional valve 1 (317) and the three-position four-way directional valve 2 (318) are connected, and the T ports of the three-position four-way directional valve 1 (317) and the three-position four-way directional valve 2 (318) are connected. The oil outlets of speed control valve 1 (313) and speed control valve 2 (314) are connected. A check valve is installed between the oil outlet of oil pump 320 and the two P oil ports; A bypass is provided between the oil outlet of the oil pump 320 and the oil tank, and an overflow valve 319 is connected to the bypass. When the three-position four-way directional valve 317 and the three-position four-way directional valve 318 are in the neutral position, oil ports A, B, and P are connected, and oil port T is closed.

[0026] A force sensor 8 is installed between the push rod of the hydraulic cylinder and the driven hub bearing housing 201, and the thrust of the hydraulic cylinder can be collected through the force sensor 8.

[0027] The oil outlet of the one-way valve is connected to an accumulator 321.

[0028] The frame 4 is provided with a guide hole, and the driven hub bearing housing 201 is provided with a guide post 9 corresponding to the guide hole. The inner diameter of the guide hole is slightly larger than the outer diameter of the guide post 9.

[0029] Specifically, in the above scheme, the speed control valve can enable the proportional pressure reducing valve to meet its usage requirements, while the speed control valve can ensure that the flow rate is the same under different pressures.

[0030] Pressure gauges are typically installed on the main circuit of a hydraulic system to monitor the pressure of the main circuit and ensure its normal operation.

[0031] The specific implementation process when using this solenoid valve assembly includes: When not started: the three-position four-way directional valve, the relief valve 319, and the proportional pressure reducing valve are all de-energized and do not output.

[0032] Retracted State: Oil pump 320 starts, energizing Y1 (left side position) of three-position four-way directional valve 317 and Y3 (left side position) of three-position four-way directional valve 318, while Y2 and Y4 are de-energized. Relief valve 319's YV1 is energized, and proportional pressure reducing valve 315's YV2 and proportional pressure reducing valve 316's YV3 are energized and maintain maximum output. Because the flow rate of oil pump 320 is greater than the discharge flow rate of the speed control valve, pressure can be built into the rod chamber of the hydraulic cylinder, causing the cylinder to retract and complete the retraction action. The retracted state is used to pull the driven hub bearing seat 201 towards the driving hub bearing seat 101, reducing the distance between them, facilitating the installation and removal of the steel belt 3.

[0033] In the extended state, oil pump 320 starts. The Y1 valve of the three-position four-way directional valve 317 and the Y3 valve of the three-position four-way directional valve 318 are de-energized, while Y2 and Y4 are energized. The YV1 valve of the relief valve 319 is energized, and the YV2 valve of the proportional pressure reducing valve 315 and the YV3 valve of the proportional pressure reducing valve 316 are de-energized and have no output. At this time, the rodless chamber of the cylinder is filled with oil, and the rod chamber of the cylinder returns oil. The oil in the rod chamber returns to the oil tank through the speed control valve. The extended state is used to push the driven hub bearing housing 201 away from the driving hub bearing housing 101, increasing the distance between them and pre-tightening the steel strip 3. During the pre-tightening of the steel strip 3, the parameters of the four displacement sensors 7 and the signals of the two force sensors 8 remain consistent.

[0034] In the initial working state, oil pump 320 starts, and Y1 and Y2 of three-position four-way directional valve 318, and Y3 and Y4 of three-position four-way directional valve 318 are not energized. Both three-position four-way directional valves are in the neutral position. YV1 of relief valve 319 is energized, and YV2 of proportional pressure reducing valve 315 and YV3 of proportional pressure reducing valve 316 are energized and output maximum pressure. That is, the pressure in the rodless chamber is P1, which equals the pressure in the rod chamber, which is P2. At this time, the output thrust of the cylinder is P1*(S1-S2), which is the minimum thrust provided by the hydraulic cylinder in the initial working state. The initial working state is used to keep the pressure in the rod chamber and rodless chamber of the first cylinder 311 and the second cylinder 312 the same to maintain the tension of the steel strip 3.

[0035] During operation, in the correction state, oil pump 320 is started. The Y1 and Y2 valves of the second three-position four-way directional valve 318, and the Y3 and Y4 valves of the second three-position four-way directional valve 318 are de-energized, both valves are in the neutral position. The YV1 valve of the relief valve 319 is energized, and the YV2 valve of the first proportional pressure reducing valve 315 and the YV3 valve of the second proportional pressure reducing valve 316 are energized and reduce pressure output as needed. At this time, the rod chamber pressure P2 meets the following range requirement: 0 ≤ P2 ≤ P1. The output thrust of the hydraulic cylinder is P1*S1 - P2*S2. Because the rod chamber pressure P2 decreases, the output thrust of the hydraulic cylinder increases, thereby changing the position of the driven hub bearing seat 201 and thus achieving the correction of the steel belt 3, until the parameters of the four displacement sensors 7 are consistent. When the rod chamber pressure P2 is 0, the maximum thrust provided by the hydraulic cylinder in the correction state is P1*S1. Therefore, the range of the thrust F of the hydraulic cylinder in the correction state is: P1*S1-P2*S2≤F≤P1*S1. Where S1 is the working area of ​​the rodless cavity and S2 is the working area of ​​the rod cavity.

[0036] Example 2: See Figure 1 , Figure 2 and Figure 4 In this embodiment, another form of solenoid valve assembly is provided, wherein the solenoid valve assembly includes one two-position four-way directional valve, one normally closed two-position two-way solenoid valve, and one normally open two-position two-way solenoid valve. The B port of the two-position four-way directional valve is connected to the inlet of the proportional pressure reducing valve, the A port is connected to the rodless chamber of the oil cylinder, the P port is connected to the oil pump 320, and the T port is connected to the oil tank. The oil outlet of the proportional pressure reducing valve is connected to the rod chamber of the oil cylinder and the oil inlet of the speed control valve, respectively. A normally closed two-position two-way solenoid valve is installed between port B and the inlet of the proportional pressure reducing valve, and a normally open two-position two-way solenoid valve is installed between port A and the inlet of the proportional pressure reducing valve. The oil outlet of the speed control valve and the oil inlet of the oil pump 320 are connected to the oil tank; The P ports of the two two-position four-way directional valves are connected, and the T ports of the two two-position four-way directional valves are connected. The oil outlets of the two speed control valves are connected; A check valve is installed between the oil outlet of the oil pump 320 and the two P oil ports. The check valve is used to prevent the system pressure oil from flowing back to the pump and to protect the pump when it is stopped or unloaded. A bypass is provided between the oil outlet of the oil pump 320 and the oil tank, and an overflow valve 319 is connected to the bypass. The overflow valve 319 serves as an overpressure protection device, allowing excess flow to overflow back into the oil tank.

[0037] like Figure 4As shown, specifically, the B port of the two-position four-way directional valve 326 is connected to the inlet of the proportional pressure reducing valve 315, the A port is connected to the rodless chamber of the first cylinder 311, the P port is connected to the oil pump 320, and the T port is connected to the oil tank. The oil outlet of the proportional pressure reducing valve 315 is connected to the rod chamber of the first oil cylinder 311 and the oil inlet of the speed regulating valve 313, respectively. A normally closed two-position two-way solenoid valve 324 is installed between port B and the inlet of proportional pressure reducing valve 315, and a normally open two-position two-way solenoid valve 322 is installed between port A and the inlet of proportional pressure reducing valve 315. The oil outlet of speed control valve 313 and the oil inlet of oil pump 320 are connected to the oil tank; The B port of the two-position four-way directional valve 327 is connected to the inlet of the proportional pressure reducing valve 316, the A port is connected to the rodless chamber of the second cylinder 312, the P port is connected to the oil pump 320, and the T port is connected to the oil tank. The oil outlet of the proportional pressure reducing valve 316 is connected to the rod chamber of the second oil cylinder 312 and the oil inlet of the speed regulating valve 314, respectively. A normally closed two-position two-way solenoid valve 325 is installed between port B and the inlet of proportional pressure reducing valve 316, and a normally open two-position two-way solenoid valve 323 is installed between port A and the inlet of proportional pressure reducing valve 316. The oil outlet of speed control valve 314 and the oil inlet of oil pump 320 are connected to the oil tank; The P ports of the three-position four-way directional valve 1 (317) and the three-position four-way directional valve 2 (318) are connected, and the T ports of the three-position four-way directional valve 1 (317) and the three-position four-way directional valve 2 (318) are connected. The oil outlets of speed control valve 1 (313) and speed control valve 2 (314) are connected.

[0038] The specific implementation process when using this solenoid valve assembly includes: When not started: the two-position four-way directional valve, normally closed two-position two-way solenoid valve, normally open two-position two-way solenoid valve, relief valve 319, and proportional pressure reducing valve should not be energized and should not output.

[0039] Retracted State: Oil pump 320 starts, energizing Y1 (left side position) of two-position four-way directional valve 326 and Y3 (left side position) of two-position four-way directional valve 327, energizing YV1 of relief valve 319, maximizing the output of YV2 of proportional pressure reducing valve 315 and YV3 of proportional pressure reducing valve 316, energizing normally closed two-position two-way solenoid valves 324 and 325 (connecting), and energizing normally open two-position two-way solenoid valves 322 and 323 (closing). Because the flow rate of oil pump 320 is greater than the discharge flow rate of the speed control valve, pressure can be built into the rod chamber of the hydraulic cylinder, causing the cylinder to retract and complete the retraction action. The retracted state is used to pull the driven hub bearing seat 201 towards the driving hub bearing seat 101 to reduce the distance between them, facilitating the installation and removal of the steel belt 3. In the extended state, oil pump 320 starts, Y1 (reset) of two-position four-way directional valve 326 and Y3 of two-position four-way directional valve 327 are de-energized (reset), YV1 of relief valve 319 is energized, YV2 of proportional pressure reducing valve 315 and YV3 of proportional pressure reducing valve 316 are de-energized and have no output, normally closed two-position two-way solenoid valve 324 and normally closed two-position two-way solenoid valve 325 are energized (connection achieved), normally open two-position two-way solenoid valve 322 and normally open two-position two-way solenoid valve 323 are both energized (closure achieved). At this time, the rodless chamber of the cylinder is filled with oil, the rod chamber of the cylinder returns oil, and the oil in the rod chamber returns to the oil tank through the speed control valve. The extended state is used to push the driven hub bearing seat 201 to move away from the driving hub bearing seat 101, increasing the distance between the two and pre-tightening the steel belt 3.

[0040] In the initial working state, oil pump 320 starts, Y1 (reset) of two-position four-way directional valve 326 and Y3 of two-position four-way directional valve 327 are de-energized (reset), YV1 of relief valve 319 is energized, YV2 of proportional pressure reducing valve 315 and YV3 of proportional pressure reducing valve 316 are energized and output maximum pressure, both normally closed two-position two-way solenoid valves are de-energized (reset closed), and both normally open two-position two-way solenoid valves are de-energized (reset open). This satisfies the condition that the rodless chamber pressure P1 equals the rod chamber pressure P2. At this time, the output thrust of the cylinder is P1*(S1-S2), which is the minimum thrust provided by the hydraulic cylinder in the initial working state. The initial working state is used to maintain the same pressure in the rod chamber and rodless chamber of the first cylinder 311 and the second cylinder 312 to maintain the tension of the steel strip 3.

[0041] During operation, in the corrective state, oil pump 320 starts, Y1 (reset) of two-position four-way directional valve 326 and Y3 of two-position four-way directional valve 327 are de-energized (reset), YV1 of relief valve 319 is energized, two normally closed two-position two-way solenoid valves are de-energized (reset closed), and two normally open two-position two-way solenoid valves are de-energized (reset open). YV2 of proportional pressure reducing valve 315 and YV3 of proportional pressure reducing valve 316 are energized and reduce pressure output as needed (determined by closed-loop control of displacement sensor 7 and force sensor). At this time, the rod chamber pressure P2 meets the following range requirement: 0≤P2≤P1. At this time, the output thrust of the oil cylinder is P1*S1-P2*S2. Since the rod chamber pressure P2 decreases, the output thrust of the oil cylinder increases, thereby changing the position of the driven hub bearing seat 201 and thus achieving the corrective action of the steel belt 3. When the pressure P2 in the rod chamber is 0, the maximum thrust provided by the hydraulic cylinder in the corrective state is P1*S1. Therefore, the range of the thrust F of the cylinder in the corrective state is: P1*S1-P2*S2≤F≤P1*S1, where S1 is the working area of ​​the rodless chamber and S2 is the working area of ​​the rod chamber.

[0042] Example 3: Based on Embodiment 1 or Embodiment 2, the displacement sensor can be the Keyence LK-G5000 series, and the force sensor can be the HBK U10M tensile / compressive force sensor. The controller can be the Siemens S7-1200.

[0043] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A belt dynamometer with a correction function, characterized in that, It includes a frame, active hub bearing seats disposed on both sides of one end of the frame, passive hub bearing seats slidably disposed on the frame, an active hub rotatably disposed on the two active hub bearing seats, a passive hub rotatably disposed on the two passive hub bearing seats, and a steel belt for transmission between the active hub and the passive hub. It also includes a correction system, which includes a monitoring device for detecting the offset of the steel strip and a controller for receiving the offset signal from the monitoring device and sending control commands to the correction actuator based on the offset signal. The correction actuator is used to correct the deviation of the steel strip according to the control command.

2. The belt dynamometer with correction function according to claim 1, characterized in that, The monitoring device includes four displacement sensors; Two displacement sensors are used to monitor the displacement of the steel belt on the driving hub, and two other displacement sensors are used to monitor the displacement of the steel belt on the driven hub.

3. The belt dynamometer with correction function according to claim 1, characterized in that, It also includes a hydraulic system for driving the correction actuator; The hydraulic system includes a first cylinder and a second cylinder symmetrically arranged on the frame for driving the driven hub bearing seat to move, and hydraulic circuits for controlling the first cylinder and the second cylinder respectively. Both hydraulic circuits include a solenoid valve assembly for reversing and maintaining pressure, and a proportional pressure reducing valve connected to the rod chamber for pressure control.

4. The belt dynamometer with correction function according to claim 3, characterized in that, The solenoid valve assembly includes a three-position four-way directional valve with a neutral position function; The three-position four-way directional valve has its B port connected to the inlet of the proportional pressure reducing valve, its A port connected to the rodless chamber of the oil cylinder, its P port connected to the oil pump, and its T port connected to the oil tank. The oil outlet of the proportional pressure reducing valve is connected to the rod chamber of the oil cylinder and the oil inlet of the speed control valve, respectively. The oil outlet of the speed control valve and the oil inlet of the oil pump are both connected to the oil tank. The P ports of the two three-position four-way directional valves are connected, and the T ports of the two three-position four-way directional valves are connected. The oil outlets of the two speed control valves are connected; A check valve is installed between the oil outlet of the oil pump and the two P oil ports. A bypass is provided between the oil pump outlet and the oil tank, and an overflow valve is connected to the bypass. When the three-position four-way directional valve is in the neutral position, ports A, B, and P are connected, while port T is closed.

5. The belt dynamometer with correction function according to claim 3, characterized in that, The solenoid valve group includes one two-position four-way directional valve, one normally closed two-position two-way solenoid valve, and one normally open two-position two-way solenoid valve. The two-position four-way directional valve has its B port connected to the inlet of the proportional pressure reducing valve, its A port connected to the rodless chamber of the oil cylinder, its P port connected to the oil pump, and its T port connected to the oil tank. The oil outlet of the proportional pressure reducing valve is connected to the rod chamber of the oil cylinder and the oil inlet of the speed control valve, respectively. A normally closed two-position two-way solenoid valve is installed between port B and the inlet of the proportional pressure reducing valve, and a normally open two-position two-way solenoid valve is installed between port A and the inlet of the proportional pressure reducing valve. The oil outlet of the speed control valve and the oil inlet of the oil pump are connected to the oil tank. The P ports of the two two-position four-way directional valves are connected, and the T ports of the two two-position four-way directional valves are connected. The oil outlets of the two speed control valves are connected; A check valve is installed between the oil outlet of the oil pump and the two P oil ports. A bypass is provided between the oil pump outlet and the oil tank, and an overflow valve is connected to the bypass.

6. The belt dynamometer with correction function according to claim 4 or 5, characterized in that, The oil outlet of the one-way valve is connected to an accumulator.

7. The belt dynamometer with correction function according to claim 1, characterized in that, The frame is provided with guide holes, and the driven hub bearing seat is provided with guide posts corresponding to the guide holes.

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