Mechanical hydraulic clutch oil drag torque measuring device and measuring method

Abstract

A mechanical hydraulic clutch oil drag torque measuring device and measuring method, relate to a kind of clutch oil drag torque measuring device, to solve the problem of inaccurate oil drag torque measurement in the existing clutch oil drag torque measurement method, which needs to disassemble and assemble small-range torsion meter connected in series, and the belt friction torque measured simultaneously contains shaft system friction torque, resulting in inaccurate oil drag torque measurement.The measuring body of the present application is installed on the clutch housing;The piston body is installed inside the oil cylinder body, and the piston and the oil cylinder tail cover form a closed piston cavity, the oil cylinder tail cover is provided with a pressure sensor, and the pressure sensor measures the liquid pressure of the piston cavity;Roller is installed at the end of piston rod, the inclined surface of guide block is in contact with roller, clutch oil drag torque makes guide block press roller, and drives piston rod to move, so that the oil pressure of piston cavity increases, the size of oil drag torque is obtained by measuring oil pressure and the distance from the contact point of guide block and roller to the rotation center of clutch, and then converted.The beneficial effect is high measurement accuracy.

Description

Technical Field

[0001] This invention relates to a device for measuring clutch hydraulic drag torque. Background Technology

[0002] In the field of mechanical transmission, when a clutch is disengaged, the input end is stationary and the output end is rotating at high speed. The transmission principle of a clutch test bench is as follows: Figure 1 As shown, the clutch contains a large amount of lubricating oil. The output end drives the outer layer of lubricating oil to rotate at high speed. Due to the viscosity of the lubricating oil, viscous friction loss occurs between the inner and outer layers of lubricating oil, which manifests as oil drag torque. The principle of clutch oil drag torque generation is as follows: Figure 2 As shown, the hydraulic drag torque increases power consumption at the output end and causes the input end to rotate, making it difficult to maintain a stationary state and increasing the difficulty of input end maintenance. Therefore, during clutch testing, it is necessary to measure the hydraulic drag torque at the output end at different speeds while the input end is stationary. The clutch hydraulic drag torque is usually about 0.5%-3% of the rated torque. Currently, a small-range standard torque meter is typically used, connected in series in the transmission shaft system of the clutch test bench for measurement. The transmission principle of measuring the hydraulic drag torque by setting a side torque meter at the output end is as follows: Figure 3 As shown, the transmission principle of measuring the hydraulic drag torque by setting a side torque meter at the input end is as follows: Figure 4 As shown, its disadvantages are: to ensure measurement accuracy, a small-range torque meter must be used. However, the small-range torque meter has a small shaft diameter, which is incompatible with the transmission shaft system of the clutch test bench. The small-range torque meter must be removed when the clutch is in operation, otherwise it will be damaged. Repeated disassembly and reassembly of the torque meter reduces the reliability of the test bench and increases the test time cost. At the same time, due to the influence of the installation position of the torque meter, the measured belt torque includes the friction torque of the bearings in the transmission shaft system of the test bench, and is not very accurate. Summary of the Invention

[0003] The purpose of this invention is to solve the problem that existing methods for measuring clutch oil drag torque require disassembly and series connection of a small-range torque meter, and that the measured torque includes shaft friction torque, leading to inaccurate oil drag torque measurement. This invention proposes a mechanical hydraulic clutch oil drag torque measuring device and method.

[0004] The present invention discloses a mechanical hydraulic clutch oil drag torque measuring device, which includes a measuring body and a guide block;

[0005] The measuring body is mounted on the clutch test box housing;

[0006] The guide block is mounted on the clutch input end;

[0007] The measuring body includes a piston body, piston seal, roller, roller pin, return spring, cylinder body, cylinder tail cover, and pressure sensor;

[0008] The cylinder body is externally fixed to the clutch test chamber housing;

[0009] The piston body is installed inside the cylinder body, and the cylinder tail cover is installed at the end of the cylinder body;

[0010] The piston body includes a piston rod, a piston, and a measuring column;

[0011] The top end of the piston rod is fixed to the bottom end of the piston; the bottom end of the measuring column is fixed to the top end of the piston, and the top end of the measuring column passes through the center of the cylinder tail cover; the piston, the cylinder body, and the cylinder tail cover form a closed piston chamber, and the piston reciprocates along the inner wall of the cylinder body.

[0012] The piston seal is a ring-shaped structure, and the piston seal is nested in the middle of the piston;

[0013] The return spring is placed between the lower part of the cylinder body and the piston; the restoring force of the return spring causes the piston to approach the cylinder tail cover.

[0014] The roller shaft is connected to the bottom end of the piston rod;

[0015] The guide block is provided with an inclined guide surface; the guide surface is in contact with the roller;

[0016] The pressure sensor is mounted on the tail cover of the cylinder and is used to measure the oil pressure inside the piston chamber.

[0017] Furthermore, the cylinder body has a breather hole at the installation position of the return spring, which allows air to freely enter the installation position of the return spring.

[0018] Furthermore, the cylinder tail cover includes a tail cover body and a pressure relief valve;

[0019] The pressure sensor is mounted on the tail cap body;

[0020] The pressure relief valve is installed on the tail cover body. When the pressure in the piston chamber is too high, the pressure relief valve opens automatically, releasing the oil in the piston chamber. At the same time as the pressure relief valve releases oil, the return spring moves the piston body upward, thereby causing the roller to disengage from the guide block, thus achieving overload protection.

[0021] Furthermore, an oil filling plug is installed on the tail cap body. After the oil filling plug is removed, the piston chamber is connected to the outside.

[0022] Furthermore, the tail cover body is fixed to the cylinder body with screws, and the tail cover body is fixed to the clutch test box housing with screws; the tail cover body is sealed to the cylinder body through the inner sealing ring; the tail cover body is sealed to the clutch test box housing through the outer sealing ring.

[0023] Furthermore, the piston rod is cylindrical, and a first guide surface 303 and a second guide surface are respectively provided on opposite sides of the piston rod;

[0024] The piston rod is positioned by a piston guide provided on the inner wall of the cylinder body.

[0025] Furthermore, the reset spring is a cylindrical helical spring structure.

[0026] Furthermore, the guide block is fixed to the clutch input end by guide block pins and guide block screws.

[0027] A method for measuring the drag torque of a mechanical hydraulic clutch, the method being implemented based on a mechanical hydraulic clutch drag torque measuring device, the method being as follows:

[0028] The measuring body is fixed to the clutch test chamber housing with screws. The clutch input end is rotated so that the guide surface of the guide block contacts the roller. The distance of the measuring column extending out of the cylinder tail cover is recorded. The radius from the contact point between the roller and the guide surface to the clutch rotation axis is obtained by conversion. The hydraulic drag torque T1 causes the guide surface to press against the roller, which in turn causes the piston to move, reducing the volume of the piston chamber and increasing the pressure. The pressure sensor measures the internal pressure P1 of the piston chamber. The pressure P1 is multiplied by the difference between the area of ​​the piston and the measuring column to obtain the tangential component of the contact force between the guide surface and the roller in the circumferential direction. The product of this tangential component and the radius of the contact point gives the value of the hydraulic drag torque T1. When the clutch output end operates at different speeds, the hydraulic drag torque T1 changes, and the internal pressure P1 of the piston chamber also changes accordingly. Therefore, by measuring the value of P1 and converting it, the value of the hydraulic drag torque T1 at different speeds of the clutch output end is obtained.

[0029] When conducting other tests on the clutch, only the measuring body needs to be removed from the clutch test chamber housing. The original installation state of the transmission shaft system of the clutch test bench should not be changed, and the test process conversion is shorter. If an overload occurs when measuring the oil drag torque T1, the internal pressure P1 of the piston chamber will exceed the opening setting value of the pressure relief valve. The piston chamber will start to drain oil, and the return spring will move the piston body and move the roller away from the guide block, so that the two no longer contact each other, thus achieving overload protection.

[0030] The beneficial effects of this invention are as follows: by replacing the torque meter with a measuring body to measure the oil drag torque, and by setting the measuring body on the clutch test box housing, the influence of the friction torque of the main drive shaft of the clutch test bench can be eliminated, and the oil drag torque of the clutch itself can be measured more accurately. It is easy to install, saves the installation time of the test equipment, and has an overload protection function for oil drag torque, reducing the probability of damage to the test equipment and improving the safety of the test. Attached Figure Description

[0031] Figure 1 The background diagram shows the transmission principle of a clutch test bench.

[0032] exist Figure 1 In this test setup, the clutch 10, used for functional testing, is located between the input gearbox 46 and the output gearbox 34. When the clutch is disengaged, the input drive motor 48 drives the input end of the clutch 10 to rotate via the input gearbox 46, and the output drive motor 38 drives the output end of the clutch 10 to rotate via the output gearbox 34. When the clutch is engaged, the input drive motor 48 drives the entire test bench to rotate.

[0033] Figure 2 Schematic diagram illustrating the principle behind clutch hydraulic drag torque;

[0034] exist Figure 2 When the clutch is disengaged, both the clutch input end 6 and the clutch output end 12 can rotate freely around the clutch rotation axis (1). The lubricating oil flows from the lubricating oil inlet 4 through the gap between the teeth 9 of the clutch input end and the teeth 13 of the clutch output end, and is discharged from the lubricating oil outlet 8. The speed of the clutch input end is V1=0, the speed of the clutch output end is V2, and V2>V1. Thus, the clutch input end 6 generates an oil drag torque T1 on the output end 12.

[0035] During the clutch torque test, the input drive motor 48 remains stationary, and the clutch input speed V1 = 0. The output drive motor 38 rotates the clutch output, and the clutch output speed is V2. Since V2 > V1, a hydraulic drag torque is generated inside the clutch. The hydraulic drag torque generally increases with the speed difference V2 - V1. The existence of the hydraulic drag torque can be observed by observing the change in the operating current of the input drive motor 48. The operating current increases with V2, indicating that the power consumption of the input drive motor 48 is increasing. In order to accurately measure the relationship between the clutch hydraulic drag torque and the speed, a torque meter needs to be installed in the transmission shaft system.

[0036] Figure 3 A schematic diagram of the transmission principle for measuring hydraulic drag torque using a side torque meter at the output end in the background technology;

[0037] exist Figure 3 In the middle, the output end side torque meter 35 is set between the output end drive motor 38 and the output end gearbox 34;

[0038] Figure 4 A schematic diagram of the transmission principle for measuring hydraulic drag torque using a side torque meter at the input end in the background technology;

[0039] exist Figure 4In the middle, the input end side torque meter 45 is set between the input end drive motor 48 and the input end gearbox 46;

[0040] Figure 5 This is a schematic diagram of the installation position of the measuring body in Specific Implementation Method 1;

[0041] Figure 6 This is a longitudinal sectional view of a mechanical hydraulic clutch oil drag torque measuring device as described in Specific Embodiment 1.

[0042] Figure 7 This is a cross-sectional view of a mechanical hydraulic clutch oil drag torque measuring device as described in Specific Embodiment 1.

[0043] Figure 8 for Figure 7 Enlarged image;

[0044] Figure 9 for Figure 8 A cross-sectional view of the roller;

[0045] Figure 10 To and Figure 8 Vertical sectional view;

[0046] Figure 11 This is a schematic diagram of the state structure of the mechanical hydraulic clutch oil drag torque measuring device in overload protection according to the first specific embodiment.

[0047] Figure 12 This is a schematic diagram of the overload protection state of a mechanical hydraulic clutch oil drag torque measuring device as described in Specific Embodiment 1.

[0048] Wherein, 1 is the clutch rotation axis; 4 is the lubricating oil inlet; 6 is the clutch input end; 8 is the lubricating oil outlet; 9 is the gear of the clutch input end; 10 is the clutch wheel; 12 is the clutch output end; 13 is the gear of the clutch output end; 34 is the output end gearbox; 35 is the output end torque meter; 38 is the output end drive motor; 45 is the input end torque meter; 46 is the input end gearbox; 48 is the input end drive motor; 100 is the measuring body; 200 is the guide block; 220 is the guide block pin; 210 is the guide block screw; 230 is the guide surface; 1000 is the clutch test chamber housing; 300 is the piston body; 301 302 is the piston rod; 303 is the first guide surface; 304 is the piston seal; 305 is the second guide surface; 310 is the roller; 320 is the roller pin; 330 is the return spring; 350 is the measuring column; 400 is the cylinder body; 420 is the cylinder piston guide; 440 is the cylinder wall; 430 is the spring mounting and positioning surface; 450 is the breather hole; 460 is the piston chamber; 500 is the cylinder tail cover; 502 is the screw; 504 is the measuring rod sealing ring; 506 is the inner sealing ring; 508 is the outer sealing ring; 520 is the tail cover body; 540 is the oil filling plug; 560 is the pressure relief valve; 580 is the pressure sensor. Detailed Implementation

[0049] Specific Implementation Method 1: Combination Figures 5 to 12 This embodiment describes a mechanical hydraulic clutch oil drag torque measuring device, which includes a measuring body 100 and a guide block 200.

[0050] The measuring body 100 is mounted on the clutch test box housing 1000;

[0051] The guide block 200 is mounted on the clutch input end 6;

[0052] The measuring body 100 includes a piston body 300, a piston seal 304, a roller 310, a roller pin 320, a return spring 330, a cylinder body 400, a cylinder tail cover 500, and a pressure sensor 580.

[0053] The cylinder body 400 is externally fixed to the clutch test box housing 1000;

[0054] The piston body 300 is installed inside the cylinder body 400, and the cylinder tail cover 500 is installed at the end of the cylinder body 400;

[0055] The piston body 300 includes a piston rod 301, a piston 302, and a measuring column 350;

[0056] The top end of piston rod 301 is fixed to the bottom end of piston 302; the bottom end of measuring column 350 is fixed to the top end of piston 302, and the top end of measuring column 350 passes through the center of cylinder tail cover 500; piston 302, cylinder body 400 and cylinder tail cover 500 form a closed piston chamber 460, and piston 302 reciprocates along the inner wall of cylinder body 400;

[0057] The piston seal 304 has a ring-shaped structure and is nested in the middle of the piston 302;

[0058] The return spring 330 is placed between the lower part of the cylinder body 400 and the piston 302; the restoring force of the return spring 330 causes the piston 302 to approach the cylinder tail cover 500.

[0059] The roller 310 is shaft-connected to the bottom end of the piston rod 301;

[0060] The guide block 200 is provided with an inclined guide surface 230; the guide surface 230 is in contact with the roller 310;

[0061] The pressure sensor 580 is mounted on the cylinder tail cover 500 and is used to measure the oil pressure inside the piston chamber 460.

[0062] In this embodiment, the measuring body 100 is fixed to the clutch test chamber housing 1000 by screws 502. The clutch input end 6 is rotated so that the guide surface 230 of the guide block 200 contacts the roller 310. The distance of the measuring column 350 extending out of the tail cover body 520 is recorded. The radius from the contact point between the roller 310 and the guide surface 230 to the clutch rotation axis 1 can be obtained by conversion. The oil drag torque T1 causes the guide surface 230 to press against the roller 310, further causing the piston body 300 to move, reducing the volume of the piston chamber 460 and increasing the pressure. The pressure sensor 58... The internal pressure P1 of the piston chamber 460 is measured. The pressure P1 is multiplied by the difference between the areas of the piston 302 and the measuring column 350, and the tangential component of the contact force between the guide surface 230 and the roller 310 in the circumferential direction is calculated. The product of this tangential component and the radius of the contact point is used to obtain the value of the hydraulic drag torque T1. When the clutch output end 12 operates at different speeds, the hydraulic drag torque T1 changes, and the internal pressure P1 of the piston chamber 460 also changes accordingly. Therefore, by measuring the value of P1 and converting it, the value of the hydraulic drag torque T1 at different speeds of the clutch output end 12 is obtained.

[0063] When conducting other tests on the clutch, only the measuring body 100 needs to be removed from the clutch test chamber housing 1000. The original installation state of the transmission shaft system of the clutch test bench should not be changed, and the test process conversion is shorter. If an overload occurs when measuring the oil drag torque T1, the internal pressure P1 of the piston chamber 460 will exceed the opening setting value of the pressure relief valve 560. The piston chamber 460 will start to drain oil. The return spring 330 will move the piston body 300 and move the roller 310 away from the guide block 200, so that the two no longer contact each other, thus realizing overload protection.

[0064] The guide surface 230 where the guide block 200 contacts the roller 310 is an inclined surface. When the guide block 200 rotates with the clutch input end 6, the roller 310 generates a component force along the axial direction of the piston rod 301 under the action of the guide surface 230, pushing the piston body 300 to move axially. The cylindrical piston rod 301 has a first guide surface 303 and a second guide surface 305 on both sides to prevent the piston rod 301 from rotating.

[0065] Figure 9 In the middle, the roller 310 is mounted on the piston rod 301 and supported by the roller pin 320. The cylindrical piston rod 301 has beveled edges on both sides to form a first guide surface 303 and a second guide surface 305. The first guide surface 303 and the second guide surface 305 are guided in the oil cylinder piston guide 420, so that the piston body 300 can only reciprocate and cannot rotate.

[0066] Figure 10 In the middle, the piston tail measuring column 350 passes through the center of the tail cover body 520 and is sealed by the measuring rod sealing ring 504; when the piston body 300 reciprocates, a part of the piston tail measuring column 350 is always exposed outside the tail cover body 520. The tail cover body 520 is also equipped with a pressure relief valve 560. When the pressure in the piston chamber 460 is too high, the pressure relief valve 560 can automatically open to release the oil in the piston chamber 460.

[0067] Figure 11 If the oil drag torque T1 is too large, the pressure relief valve 560 will release oil. At the same time as the pressure relief valve 560 releases oil, the reset spring will move the piston body 300 upward, thereby causing the roller 310 to disengage from the guide block 200, thus achieving overload protection.

[0068] Figure 12 After the pressure relief valve 560 releases oil, the clutch input end 6 can rotate continuously under the action of the oil drag torque T1.

[0069] In a preferred embodiment, the cylinder body 400 has a breather hole 450 at the mounting position of the return spring 330, which allows air to freely enter the mounting position of the return spring 330.

[0070] In this embodiment, the setting of the breather oil hole 450 ensures smooth reciprocating motion of the piston body 300.

[0071] In a preferred embodiment, the cylinder tail cover 500 includes a tail cover body 520 and a pressure relief valve 560;

[0072] The pressure sensor 580 is mounted on the tail cover body 520;

[0073] The pressure relief valve 560 is installed on the tail cover body 520. When the pressure in the piston chamber 460 is too high, the pressure relief valve 560 automatically opens, releasing the oil in the piston chamber 460. At the same time as the pressure relief valve 560 releases oil, the return spring moves the piston body 300 upward, thereby causing the roller 310 to disengage from the guide block 200, thus achieving overload protection.

[0074] In a preferred embodiment, an oil filling plug 540 is installed on the tail cap body 520. After the oil filling plug 540 is removed, the piston chamber 460 is connected to the outside.

[0075] In a preferred embodiment, the tail cover body 520 is fixed to the cylinder body 400 by screws 502, and the tail cover body 520 is fixed to the clutch test chamber housing 1000 by screws 502; the tail cover body 520 is sealed to the cylinder body 400 by an inner sealing ring 506; and the tail cover body 520 is sealed to the clutch test chamber housing 1000 by an outer sealing ring 508.

[0076] In a preferred embodiment, the piston rod 301 is cylindrical, and a first guide surface 303 and a second guide surface 305 are respectively provided on opposite sides of the piston rod 301;

[0077] The piston rod 301 is positioned by a cylinder piston guide 420 provided on the inner wall of the cylinder body 400.

[0078] In a preferred embodiment, the return spring 330 is a cylindrical helical spring structure.

[0079] In a preferred embodiment, the guide block 200 is fixed to the clutch input end 6 by guide block pins 220 and guide block screws 210.

[0080] Specific Implementation Method Two: A method for measuring the drag torque of a mechanical hydraulic clutch. This method is based on the mechanical hydraulic clutch drag torque measuring device described in Specific Implementation Method One. The method is as follows:

[0081] The measuring body 100 is fixed to the clutch test chamber housing 1000 with screws. The clutch input end 6 is rotated so that the guide surface 230 of the guide block 200 contacts the roller 310. The distance of the measuring column 350 extending out of the cylinder tail cover 500 is recorded. The radius from the contact point between the roller 310 and the guide surface 230 to the rotation axis of the clutch 10 is obtained by calculation. The hydraulic torque T1 causes the guide surface 230 to press against the roller 310, which in turn causes the piston body 300 to move, reducing the volume of the piston chamber 460 and increasing the pressure. The pressure sensor 580 measures the piston volume. The pressure P1 inside the piston cavity 460 is multiplied by the difference between the areas of the piston 302 and the measuring column 350 to obtain the tangential component of the contact force between the guide surface 230 and the roller 310 in the circumferential direction. The product of this tangential component and the radius of the contact point gives the value of the hydraulic drag torque T1. When the clutch output end 12 operates at different speeds, the hydraulic drag torque T1 changes, and the pressure P1 inside the piston cavity 460 also changes accordingly. Therefore, by measuring the value of P1 and converting it, the value of the hydraulic drag torque T1 at different speeds of the clutch output end 12 can be obtained.

[0082] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A mechanical hydraulic clutch oil drag torque measuring device, the measuring device comprising a measuring body (100) and a guide block (200). The measuring body (100) is mounted on the clutch test box housing (1000); The guide block (200) is mounted on the clutch input end (6); Its features are, The measuring body (100) includes a piston body (300), a piston seal (304), a roller (310), a roller pin (320), a return spring (330), a cylinder body (400), a cylinder tail cover (500), and a pressure sensor (580). The cylinder body (400) is externally fixed to the clutch test box housing (1000); The piston body (300) is installed inside the cylinder body (400), and the cylinder tail cover (500) is installed at the end of the cylinder body (400); The piston body (300) includes a piston rod (301), a piston (302), and a measuring column (350). The top end of the piston rod (301) is fixed to the bottom end of the piston (302); the bottom end of the measuring column (350) is fixed to the top end of the piston (302), and the top end of the measuring column (350) passes through the center of the cylinder tail cover (500); the piston (302), the cylinder body (400), and the cylinder tail cover (500) form a closed piston chamber (460), and the piston (302) reciprocates along the inner wall of the cylinder body (400); The piston seal (304) has an annular structure and is nested in the middle of the piston (302); The return spring (330) is placed between the lower part of the cylinder body (400) and the piston (302); the restoring force of the return spring (330) causes the piston (302) to approach the cylinder tail cover (500). The roller (310) is axled to the bottom end of the piston rod (301); The guide block (200) is provided with an inclined guide surface (230); the guide surface (230) is in contact with the roller (310); The pressure sensor (580) is mounted on the cylinder tail cover (500) and is used to measure the oil pressure inside the piston chamber (460).

2. The mechanical hydraulic clutch oil drag torque measuring device according to claim 1, characterized in that, The cylinder body (400) has a breather hole (450) at the mounting position of the return spring (330), which allows air to freely enter the mounting position of the return spring (330).

3. The mechanical hydraulic clutch oil drag torque measuring device according to claim 1, characterized in that, The cylinder tail cover (500) includes a tail cover body (520) and a pressure relief valve (560). The pressure sensor (580) is mounted on the tail cap body (520); The pressure relief valve (560) is installed on the tail cover body (520). When the pressure in the piston chamber (460) is too high, the pressure relief valve (560) automatically opens, allowing the oil in the piston chamber (460) to be released. At the same time as the pressure relief valve (560) releases oil, the return spring causes the piston body (300) to move upward, thereby causing the roller (310) to disengage from the guide block (200), thus achieving overload protection.

4. The mechanical hydraulic clutch oil drag torque measuring device according to claim 3, characterized in that, An oil filling plug (540) is installed on the tail cap body (520). After the oil filling plug (540) is removed, the piston chamber (460) is connected to the outside.

5. The mechanical hydraulic clutch oil drag torque measuring device according to claim 1, characterized in that, The tail cover body (520) is fixed to the cylinder body (400) by screws (502), and the tail cover body (520) is fixed to the clutch test box housing (1000) by screws (502); the tail cover body (520) is sealed to the cylinder body (400) by the inner sealing ring (506); the tail cover body (520) is sealed to the clutch test box housing (1000) by the outer sealing ring (508).

6. The mechanical hydraulic clutch oil drag torque measuring device according to claim 1, characterized in that, The piston rod (301) is cylindrical, and a first guide surface (303) and a second guide surface (305) are respectively provided on opposite sides of the piston rod (301). The piston rod (301) is positioned by a cylinder piston guide (420) provided on the inner wall of the cylinder body (400).

7. The mechanical hydraulic clutch oil drag torque measuring device according to claim 1, characterized in that, The reset spring (330) is a cylindrical helical spring structure.

8. The mechanical hydraulic clutch oil drag torque measuring device according to claim 1, characterized in that, The guide block (200) is fixed to the clutch input end (6) by the guide block pin (220) and the guide block screw (210).

9. A method for measuring the drag torque of a mechanical-hydraulic clutch, the method being implemented based on the mechanical-hydraulic clutch drag torque measuring device according to claim 1, characterized in that, The measurement method is as follows: The measuring body (100) is fixed to the clutch test chamber housing (1000) with screws. The clutch input end (6) is rotated so that the guide surface (230) of the guide block (200) contacts the roller (310). The distance of the measuring column (350) extending out of the cylinder tail cover (500) is recorded. The radius from the contact point between the roller (310) and the guide surface (230) to the rotation axis of the clutch (10) is obtained by calculation. The oil drag torque T1 causes the guide surface (230) to press the roller (310), which in turn causes the piston body (300) to move, reducing the volume of the piston chamber (460) and increasing the pressure. The pressure sensor ( 580) Measure the internal pressure P1 of the piston chamber (460). Multiply the pressure P1 by the difference between the area of ​​the piston (302) and the measuring column (350) to obtain the tangential component of the contact force between the guide surface (230) and the roller (310) in the circumferential direction. The product of this tangential component and the radius of the contact point is used to obtain the value of the oil drag torque T1. When the clutch output end (12) operates at different speeds, the oil drag torque T1 changes, and the internal pressure P1 of the piston chamber (460) also changes accordingly. Therefore, by measuring the value of P1 and converting it, the value of the oil drag torque T1 at different speeds of the clutch output end (12) is obtained.

Images