Taylor couette poiseuille flow rotational torque measuring device and measuring method

Abstract

The present disclosure relates to the technical field of experimental device manufacturing, and particularly provides a Taylor-Kutateladze flow rotating torque measuring device and a measuring method, comprising a stator mechanism, a rotor mechanism, a power transmission mechanism and a torque measuring mechanism, the inside of the stator mechanism is provided with a measuring chamber; the rotor mechanism is arranged in the measuring chamber, and the rotor mechanism and the stator mechanism have a gap therebetween, and the Taylor-Kutateladze flow can be formed by a cooling medium in the gap; the power input end of the power transmission mechanism is connected with a motor; the first end of the torque measuring mechanism is connected with the rotor mechanism, and the second end is connected with the power transmission mechanism; the motor drives the power transmission mechanism to rotate, the power transmission mechanism drives the torque measuring mechanism to rotate, the torque measuring mechanism drives the rotor mechanism to rotate, and the torque measuring mechanism measures the rotating torque change of the rotor mechanism. The present disclosure can accurately measure the rotating torque of the Taylor-Kutateladze flow, and provide a reference basis for motor cooling structure design, optimization, power generation efficiency improvement and the like.

Description

Technical Field

[0001] This disclosure relates to the field of experimental device manufacturing technology, and in particular to a Taylor-Courtberg blade flow rotation torque measuring device and method, which can be applied to the measurement of electric vehicle motors. Background Technology

[0002] Electric motors are the power devices in the new energy field. Driven by the pursuit of smaller size and higher power, the speed of electric motors has been rising all the way up, from two or three thousand revolutions per minute in the early days to tens of thousands or even hundreds of thousands of revolutions per minute. However, the loss of electric motors increases geometrically with the speed. The heat generated by the high loss of electric motors causes the temperature of the motor to rise rapidly. It is necessary to design a good motor cooling method for cooling. At present, the commonly used cooling method for high-speed motors is internal oil cooling.

[0003] However, using internal oil cooling to cool the motor presents new challenges to motor design due to the rotor-stator clearance. Flow losses caused by the cooling medium passing through this clearance reduce the motor's output power. To achieve the required output power, these losses must be considered. The flow of the cooling medium between the rotor and stator at high speed is known as the Taylor-Coolter-Poise flow. Depending on the rotor speed and axial velocity, the Taylor-Coolter-Poise flow exhibits diverse flow patterns and significant flow losses, further reducing the motor's power output. Therefore, it is necessary to qualitatively and quantitatively assess the rotational torque generated by the medium passing through the rotor-stator clearance. Summary of the Invention

[0004] This disclosure is made in view of the above-mentioned problems. This disclosure provides a device and method for measuring the rotating torque of a Taylor-Couterberg blade flow.

[0005] According to one aspect of this disclosure, a Taylor-Couterberg blade flow rotation torque measuring device is provided, comprising:

[0006] A stator mechanism, wherein a measuring chamber is provided inside the stator mechanism;

[0007] A rotor mechanism is disposed in the measuring chamber and is rotatable relative to the stator mechanism. There is a gap between the rotor mechanism and the stator mechanism, and a Taylor-Couterberg flow can be formed in the gap by a cooling medium.

[0008] A power transmission mechanism, wherein the power input end of the power transmission mechanism is connected to a motor;

[0009] A torque measuring mechanism is provided in the measuring chamber, with its first end connected to the rotor mechanism and its second end connected to the power transmission mechanism.

[0010] The motor drives the power transmission mechanism to rotate, which in turn drives the torque measuring mechanism to rotate. The torque measuring mechanism then drives the rotor mechanism to rotate. The torque measuring mechanism measures the change in the rotational torque of the rotor mechanism, thereby obtaining the rotational torque generated by the Taylor Cotepure blade flow in the gap.

[0011] Furthermore, according to one aspect of the Taylor-Couterberg blade flow rotation torque measuring device of this disclosure, the stator mechanism includes:

[0012] The first outer cylinder, the rotor mechanism is disposed inside the first outer cylinder;

[0013] A front end cover is provided at the first end of the first outer cylinder, and the front end cover is provided with a liquid inlet pipe for inputting cooling medium.

[0014] Furthermore, according to the Taylor-Couterberg blade flow rotation torque measuring device of one aspect of this disclosure, the stator mechanism further includes:

[0015] The second outer cylinder is connected to the second end of the first outer cylinder. The cylinder wall of the second outer cylinder is provided with a drain pipe for outputting cooling medium. The torque measuring mechanism is located inside the second outer cylinder.

[0016] Furthermore, according to one aspect of the Taylor Cottonbury blade flow rotation torque measuring device of this disclosure, the cylinder wall of the first outer cylinder is provided with thermocouple screws for connecting thermocouples.

[0017] Furthermore, according to one aspect of the Taylor-Couterberg blade flow rotation torque measuring device of this disclosure, the rotor mechanism includes:

[0018] A first drive shaft, the second end of which is connected to the torque measuring mechanism;

[0019] An inner cylinder is mounted on the first drive shaft, which is capable of driving the inner cylinder to rotate. The outer circumference of the inner cylinder and the inner circumference of the first outer cylinder have the gap.

[0020] Furthermore, according to one aspect of this disclosure, the inner cylinder with different axial lengths can be replaced to change the axial length of the gap, and a bushing is provided on the first drive shaft for axially limiting the inner cylinder;

[0021] And / or, the inner cylinder may be replaced with one of different radii to change the width of the gap.

[0022] Furthermore, according to one aspect of the Taylor Cottorp slewing turbine rotation torque measuring device of this disclosure, the interior of the first outer cylinder is provided with:

[0023] A first bearing housing, in which a first bearing is disposed, the first bearing supporting the first end of the first transmission shaft, and the first bearing housing having a through hole through which a cooling medium can flow;

[0024] The second bearing housing contains a second bearing that supports the second end of the first drive shaft. The second bearing housing has through holes through which cooling medium can flow.

[0025] Furthermore, according to one aspect of this disclosure, the Taylor-Couterberg blade flow rotation torque measuring device includes:

[0026] A torque sensor is used to measure the change in rotational torque of the inner cylinder;

[0027] A first coupling connects the torque sensor and the second end of the first drive shaft;

[0028] A second coupling connects the torque sensor and the power transmission mechanism;

[0029] The first coupling and the second coupling are flexible couplings.

[0030] Furthermore, according to one aspect of the Taylor-Couterberg blade flow rotation torque measuring device of this disclosure, the power transmission mechanism includes:

[0031] A magnetic torque transmitter, used to connect to a motor;

[0032] The second drive shaft has a first end connected to the second coupling and a second end connected to the magnetic torque transmitter, which transmits rotational torque to the torque measuring mechanism.

[0033] Furthermore, according to one aspect of the Taylor Cottonberg blade flow rotation torque measuring device of this disclosure, a third bearing seat is provided inside the second outer cylinder, a third bearing is provided in the third bearing seat, the third bearing supports the first end of the second drive shaft, and the third bearing seat is a closed plate structure.

[0034] Furthermore, according to the Taylor-Couterberg blade flow rotation torque measuring device of one aspect of this disclosure, the stator mechanism further includes:

[0035] The third outer cylinder has its first end connected to the second end of the second outer cylinder. The magnetic torque transmitter is located at the second end of the third outer cylinder. The third outer cylinder has a fourth bearing seat inside, and a fourth bearing is located in the fourth bearing seat. The fourth bearing supports the second end of the second transmission shaft.

[0036] Furthermore, according to one aspect of the Taylor-Couterberg blade flow rotation torque measuring device of this disclosure, the magnetic torque transmitter includes:

[0037] An outer rotor is used to connect to a motor, and a first magnetic device is provided on the inner circumference of the outer rotor.

[0038] An inner rotor is connected to the second end of the second drive shaft. A second magnetic device is provided on the outer circumference of the inner rotor. The inner rotor extends into the interior of the outer rotor. The outer rotor drives the inner rotor to rotate through magnetic force.

[0039] An isolation cover is disposed between the outer rotor and the inner rotor, connecting and sealing the second end of the third outer cylinder.

[0040] Furthermore, according to the Taylor-Couterberg blade flow rotation torque measuring device of one aspect of this disclosure, the stator mechanism further includes:

[0041] A pressure ring is used to fix the isolation cover to the second end of the third outer cylinder to prevent leakage of the cooling medium.

[0042] According to another aspect of this disclosure, a method for measuring the rotating torque of a Taylor-Couterberg blade flow is provided, comprising the following steps:

[0043] S1: The motor drives the magnetic torque transmitter to rotate, and the magnetic torque transmitter transmits the rotational torque of the motor to the rotor mechanism.

[0044] S2: When the rotor mechanism rotates at low speed, the cooling medium flows in from the inlet pipe of the front cover, passes through the gap between the inner cylinder and the first outer cylinder, and then flows out through the drain pipe of the second outer cylinder, forming a Taylor-Couterberg flow in the gap.

[0045] S3: When the rotor mechanism speed is low, the flow of the cooling medium in the gap is laminar. The reading M of the torque sensor is recorded, which is the rotational torque of the inner cylinder under this flow state.

[0046] S4: By changing the speed of the motor, the reading M of the torque sensor corresponding to different speeds is measured, thereby obtaining the rotational torque of the inner cylinder at different speeds;

[0047] S5: By changing the flow rate of the cooling medium through the inlet pipe, the reading M of the torque sensor corresponding to different axial flow rates is measured to obtain the rotational torque of the inner cylinder under different axial flow rates.

[0048] S6: By changing the axial length of the inner cylinder, the reading M of the torque sensor corresponding to different axial lengths is measured to obtain the rotational torque of the inner cylinder under different axial lengths.

[0049] Furthermore, the method for measuring the rotating torque of a Taylor-Couterberg blade flow according to one aspect of this disclosure also includes the following steps:

[0050] S7: Replace the inner cylinder with a different radius, and execute steps S3, S4 and S5 to obtain the rotational torque of the inner cylinder corresponding to different rotational speeds, axial flow rates and axial lengths under different radius ratios.

[0051] The Taylor-Couter-Purple blade flow rotation torque measuring device and method according to the embodiments of this disclosure can study the rotation torque characteristics of Taylor-Couter-Purple blade flow under different rotational speeds, geometric structures, inlet flow rates, and axial lengths, and carry out related theoretical analysis and experimental research. The above research has important engineering and scientific significance for reducing the oil churning loss between the stator and rotor of the motor and improving the motor drive efficiency and power generation efficiency.

[0052] It should be understood that both the foregoing general description and the following detailed description are exemplary and intended to provide further illustration of the claimed technology. Attached Figure Description

[0053] The above and other objects, features, and advantages of this disclosure will become more apparent from the more detailed description of the embodiments thereof in conjunction with the accompanying drawings. The drawings are provided to further illustrate the embodiments of this disclosure and form part of the specification. They are used together with the embodiments of this disclosure to explain the disclosure and do not constitute a limitation thereof. In the drawings, the same reference numerals generally represent the same components or steps.

[0054] Figure 1 This is a right-side schematic diagram of a Taylor-Couterberg blade flow rotation torque measuring device according to an embodiment of the present disclosure;

[0055] Figure 2 for Figure 1 A cross-sectional view along AA;

[0056] Figure 3 This is a schematic flowchart of a method for measuring the rotational torque of a Taylor-Couterberg blade flow according to an embodiment of the present disclosure.

[0057] Explanation of reference numerals in the attached figures:

[0058] 100: Taylor Cottonberg blade flow rotation torque measuring device, 1: front end cover, 2: liquid inlet pipe, 3: first outer cylinder, 31: first bearing seat, 32: first bearing, 33: second bearing seat, 34: second bearing, 4: first sealing ring, 5: first drive shaft, 51: bushing, 6: inner cylinder, 7: key, 8: thermocouple screw, 9: second outer cylinder, 91: third bearing seat, 92: third bearing, 93: mounting base, 10: second sealing ring, 11: torque sensor, 12: first coupling, 13: second coupling, 14: drain pipe, 15: second drive shaft, 16: third outer cylinder, 161: fourth bearing seat, 162: fourth bearing, 17: third sealing ring, 18: pressure ring, 19: magnetic torque transmitter, 191: outer rotor, 192: inner rotor, 193: isolation cover, 20: clearance. Detailed Implementation

[0059] To make the objectives, technical solutions, and advantages of this disclosure more apparent, exemplary embodiments according to this disclosure will now be described in detail with reference to the accompanying drawings. Obviously, the described embodiments are merely some embodiments of this disclosure, and not all embodiments of this disclosure. It should be understood that this disclosure is not limited to the exemplary embodiments described herein.

[0060] This disclosure provides a Taylor-Couter-Poseidon blade flow rotational torque measuring device and method, which can accurately measure the rotational torque of Taylor-Couter-Poseidon blade flow, providing a reference for motor cooling structure design, optimization, drive efficiency, and power generation efficiency improvement.

[0061] The rotational torque of a Taylor-Coot-Poseidon flow is influenced by a combination of factors, such as rotor speed, clearance geometry, axial flow velocity, and axial length. However, current research on rotational torque measurement primarily focuses on Taylor-Coot flows without superimposed axial flow, and the measurement techniques involved do not effectively eliminate the effect of additional rotational torque, resulting in inaccurate values ​​for the rotational torque of Taylor-Coot-Poseidon flows and insufficient precision in the measurement results. Currently, there is no high-precision Taylor-Coot-Poseidon flow rotational torque measurement device available in China, and existing devices lack the capability to change the axial length of the device.

[0062] The embodiments of this disclosure will now be described in detail with reference to the accompanying drawings.

[0063] like Figure 1 , Figure 2 As shown, this disclosure provides a Taylor Cottorpoise blade flow rotary torque measuring device 100, including: a stator mechanism, a rotor mechanism, a power transmission mechanism, and a torque measuring mechanism;

[0064] The stator mechanism is fixed in place, and a measuring chamber is set inside the stator mechanism;

[0065] The rotor mechanism simulates the rotor of an electric motor and can be driven to rotate. The rotor mechanism is set in the measuring chamber and can rotate relative to the stator mechanism. There is a gap 20 between the rotor mechanism and the stator mechanism. A Taylor-Couterberg vane flow can be formed in the gap 20 through the cooling medium, which can be cooling oil.

[0066] The power input end of the power transmission mechanism is connected to a motor, which is a drive motor, and the power output end is connected to a torque measuring mechanism. During the measurement process, the power transmission mechanism is in a rotating state.

[0067] The torque measuring mechanism is located in the measuring chamber. The first end of the torque measuring mechanism is connected to the rotor mechanism, and the second end is connected to the power transmission mechanism. During the measurement process, the torque measuring mechanism is in a rotating state.

[0068] The motor drives the power transmission mechanism to rotate, which in turn drives the torque measuring mechanism to rotate. The torque measuring mechanism then drives the rotor mechanism to rotate. The torque measuring mechanism measures the change in the rotational torque of the rotor mechanism, which yields the rotational torque generated by the Taylor Cotepure blade flow in the gap 20.

[0069] The principle of measuring the rotational torque generated by the Taylor Coulter-Pursch blade flow is as follows: Before the cooling medium is input, the torque measuring mechanism measures the rotational torque of the rotor mechanism to obtain an initial value. After the cooling medium is input, under the influence of the Taylor Coulter-Pursch blade flow, the torque measuring mechanism measures the rotational torque of the rotor mechanism to obtain a change value. By comparing the initial value and the change value, the rotational torque generated by the Taylor Coulter-Pursch blade flow in the gap 20 can be obtained.

[0070] The Taylor-Couter-Purple blade flow rotation torque measuring device in this embodiment can accurately measure the rotation torque of the Taylor-Couter-Purple blade flow, providing a reference for motor cooling structure design, optimization, drive efficiency, and power generation efficiency improvement.

[0071] In some possible implementations, such as Figure 1 , Figure 2 As shown, the stator mechanism includes: a first outer cylinder 3 and a front end cover 1;

[0072] The first outer cylinder 3 simulates the outer shell of the motor. The rotor mechanism is located inside the first outer cylinder 3 and can rotate inside the first outer cylinder 3. Flanges are provided at both ends of the first outer cylinder 3 along its axial direction.

[0073] The front cover 1 simulates the end cover of the motor. The front cover 1 is set at the first end of the first outer cylinder 3. The front cover 1 is provided with a liquid inlet pipe 2 for inputting cooling medium. The edge of the front cover 1 is provided with a flange, which is fixedly connected to the first outer cylinder 3 by the flange and bolts.

[0074] The inlet pipe 2 is located in the middle of the front cover 1, directly opposite the axis of the rotor mechanism. The input cooling medium can spread outwards from the middle and enter the gap 20. A sealing structure needs to be provided at the connection between the inlet pipe 2 and the front cover 1 to prevent leakage of the cooling medium.

[0075] The front cover 1 has an insertion section on the side facing the first outer cylinder 3. The insertion section extends into the interior of the first outer cylinder 3. A sealing groove is provided on the outer circumference of the insertion section. A first sealing ring 4 is provided in the sealing groove to seal the connection position between the front cover 1 and the first outer cylinder 3 and prevent the cooling medium from leaking.

[0076] Because of the connection of the plug section, the front cover 1 can move outward from the first outer cylinder 3 by an appropriate distance, with a movement range of 50–200 mm, to achieve precise locking of the first bearing seat 31.

[0077] In some possible implementations, such as Figure 2 As shown, the first outer cylinder 3 is provided with thermocouple screws 8 on its cylinder wall for connecting thermocouples, which can measure the temperature change of the first outer cylinder 3 and simulate the temperature rise during the operation of the motor. In addition, further experimental research can be carried out on the heat transfer characteristics of the Taylor-Couterberg blade flow.

[0078] In some possible implementations, such as Figure 2 As shown, the rotor mechanism includes: a first drive shaft 5 and an inner cylinder 6;

[0079] The first drive shaft 5 simulates the main shaft of the motor, and the second end of the first drive shaft 5 is connected to a torque measuring mechanism.

[0080] The inner cylinder 6 simulates the rotor coil or permanent magnet of an electric motor. The inner cylinder 6 is mounted on the first drive shaft 5, which can drive the inner cylinder 6 to rotate. There is a gap 20 between the outer circumference of the inner cylinder 6 and the inner circumference of the first outer cylinder 3.

[0081] The inner cylinder 6 and the first drive shaft 5 can be connected by a key 7 to maintain circumferential fixation. Axial fixation can be achieved by means of a step on the first drive shaft 5 and a bushing 51.

[0082] In some possible implementations, such as Figure 2 As shown, the inner cylinder 6 with different axial lengths can be replaced to change the axial length of the gap 20. A bushing 51 is provided on the first drive shaft 5. The bushing 51 is used to limit the axial movement of the inner cylinder 6. When the inner cylinder 6 is replaced, the bushing 51 also needs to be replaced with a different axial length to ensure the overall rigidity of the rotor mechanism. The standard length modules of the inner cylinder 6 are: 50mm, 100mm, and 150mm.

[0083] The inner cylinder 6 can be replaced with one of different radii to change the width of the gap 20. When the radius of the inner cylinder 6 is reduced, the width of the gap 20 increases, and when the radius of the inner cylinder 6 is increased, the width of the gap 20 decreases.

[0084] By changing the axial length and radius of the inner cylinder 6, the effects of axial length and width on the rotational torque of the Taylor-Couterbury blade flow can be studied, thus expanding the range of experimental parameters.

[0085] In some possible implementations, such as Figure 2 As shown, the interior of the first outer cylinder 3 is provided with: a first bearing seat 31 and a second bearing seat 33;

[0086] A first bearing 32 is provided in the first bearing housing 31. The first bearing 32 supports the first end of the first drive shaft 5. The first bearing housing 31 is provided with a through hole through which the cooling medium can flow. The first bearing housing 31 is not an integral structure with the first outer cylinder 3. It can be tightly connected with the first outer cylinder 3 and is axially limited by the front end cover 1. It remains fixed inside the first outer cylinder 3. The first end of the first drive shaft 5 is provided with a nut and a bearing sleeve to axially limit the first bearing 32.

[0087] The second bearing housing 33 houses the second bearing 34, which supports the second end of the first drive shaft 5. The second bearing housing 33 has through holes through which cooling medium can flow. The second bearing housing 33 is an integral structure with the first outer cylinder 3 and remains fixed inside the first outer cylinder 3. The second end of the first drive shaft 5 is provided with a nut and a bearing sleeve to axially limit the second bearing 34.

[0088] In some possible implementations, such as Figure 1 , Figure 2 As shown, the stator mechanism also includes: a second outer cylinder 9;

[0089] Flanges are provided at both ends of the second outer cylinder 9. The second outer cylinder 9 is connected to the second end of the first outer cylinder 3 and can be fixedly connected by flanges and bolts. A drain pipe 14 is provided on the cylinder wall of the second outer cylinder 9 for outputting cooling medium. The torque measuring mechanism is located inside the second outer cylinder 9.

[0090] The second outer cylinder 9 has an insertion section on the side facing the first outer cylinder 3. The insertion section extends into the interior of the first outer cylinder 3. A sealing groove is provided on the outer circumference of the insertion section. A second sealing ring 10 is provided in the sealing groove to seal the connection position between the second outer cylinder 9 and the first outer cylinder 3 and prevent leakage of the cooling medium.

[0091] In some possible implementations, such as Figure 2 As shown, the torque measuring mechanism includes: a torque sensor 11, a first coupling 12, and a second coupling 13;

[0092] The torque sensor 11 is used to measure the change in rotational torque of the inner cylinder 6; the second outer cylinder 9 is provided with a mounting base 93 on its wall, and a signal transmission and power supply structure can be correspondingly set on the mounting base 93 to transmit the measurement signal to the outside. The mounting base 93 is provided with a round hole to connect to the interior of the second outer cylinder 9.

[0093] The first coupling 12 connects the torque sensor 11 and the second end of the first drive shaft 5, and is used to transmit rotational torque between the two.

[0094] The second coupling 13 connects the torque sensor 11 and the power transmission mechanism, and is used to transmit rotational torque between the two.

[0095] The first coupling 12 and the second coupling 13 can be flexible couplings to compensate for the relative axial, radial and angular displacements of the two shafts and avoid damage to the torque sensor 11.

[0096] The power transmission mechanism, torque measurement mechanism and rotor mechanism form a series torque transmission chain. The torque sensor 11 measures the overall torque value in real time. The data is led out through the round hole of the rear mounting base 93 and transmitted to the external data acquisition system. The measurement accuracy reaches ±0.2%FS.

[0097] In some possible implementations, such as Figure 2 As shown, the power transmission mechanism includes: a magnetic torque converter 19 and a second drive shaft 15;

[0098] The magnetic torque transmitter 19 transmits rotational torque through magnetic force. It has no hard connection inside, realizing non-contact torque transmission. The magnetic torque transmitter 19 is used to connect to the motor.

[0099] The first end of the second drive shaft 15 is connected to the second coupling 13, and the second end is connected to the magnetic torque transmitter 19, which transmits the rotational torque to the torque measuring mechanism.

[0100] In some possible implementations, such as Figure 2 As shown, a third bearing seat 91 is provided inside the second outer cylinder 9, and a third bearing 92 is provided in the third bearing seat 91. The third bearing 92 supports the first end of the second transmission shaft 15. The third bearing seat 91 is a closed plate structure, which can prevent the cooling medium from passing through the third bearing seat 91.

[0101] The third bearing housing 91 and the second outer cylinder 9 are an integral structure, and remain fixed inside the second outer cylinder 9. The first end of the second drive shaft 15 is provided with a nut and a bearing sleeve to axially limit the third bearing 92.

[0102] In some possible implementations, such as Figure 2 As shown, the stator mechanism also includes: a third outer cylinder 16;

[0103] Flanges are provided at both ends of the third outer cylinder 16 along its axial direction. The first end of the third outer cylinder 16 is connected to the second end of the second outer cylinder 9. The connection can be fixed by flanges and bolts. The magnetic torque transmitter 19 is provided at the second end of the third outer cylinder 16. A fourth bearing seat 161 is provided inside the third outer cylinder 16. A fourth bearing 162 is provided in the fourth bearing seat 161. The fourth bearing 162 supports the second end of the second drive shaft 15.

[0104] The fourth bearing housing 161 is not an integral structure with the third outer cylinder 16. It can be tightly connected with the third outer cylinder 16 and is axially limited by the step on the inner circumference of the third outer cylinder 16, so that it remains fixed inside the third outer cylinder 16. The second end of the second drive shaft 15 is provided with a bearing sleeve to axially limit the fourth bearing 162.

[0105] The third outer cylinder 16 has a plug-in section on the side facing the second outer cylinder 9. The plug-in section extends into the interior of the second outer cylinder 9. A sealing groove is provided on the outer circumference of the plug-in section. A third sealing ring 17 is provided in the sealing groove to seal the connection position between the third outer cylinder 16 and the second outer cylinder 9 and prevent leakage of the cooling medium.

[0106] In some possible implementations, such as Figure 2 As shown, the magnetic torsion transmitter 19 includes: an outer rotor 191, an inner rotor 192, and an isolation cover 193;

[0107] The outer rotor 191 is used to connect the motor, and the inner circumference of the outer rotor 191 is provided with a first magnetic device.

[0108] The inner rotor 192 is connected to the second end of the second drive shaft 15. A second magnetic device is provided on the outer circumference of the inner rotor 192. The inner rotor 192 extends into the interior of the outer rotor 191. The outer rotor 191 drives the inner rotor 192 to rotate through magnetic force, thereby realizing non-contact torque transmission.

[0109] The isolation cover 193 can be made of fluororubber and can withstand a fluid pressure of 1.5MPa. The isolation cover 193 is located between the outer rotor 191 and the inner rotor 192, connecting and sealing the second end of the third outer cylinder 16.

[0110] The isolation cover 193 forms a closed cavity at the second end of the third outer cylinder 16, converting the dynamic seal into a static seal and completely preventing leakage of the cooling medium.

[0111] In some possible implementations, such as Figure 2 As shown, the stator mechanism also includes: a pressure ring 18;

[0112] The pressure ring 18 is fixedly connected to the second end of the third outer cylinder 16 by bolts, thereby fixing the isolation cover 193 to the second end of the third outer cylinder 16 to prevent leakage of the cooling medium. A sealing groove and a sealing ring can also be provided at the second end of the third outer cylinder 16 to further improve the sealing performance of the connection.

[0113] In some possible implementations, such as Figure 3 As shown, the Taylor-Couterberg blade flow rotation torque measurement method includes the following steps:

[0114] S1: The motor drives the magnetic torque transmitter to rotate, and the magnetic torque transmitter transmits the rotational torque of the motor to the rotor mechanism.

[0115] S2: When the rotor mechanism rotates at low speed, the cooling medium flows in from the inlet pipe of the front cover, passes through the gap between the inner cylinder and the first outer cylinder, and then flows out through the drain pipe of the second outer cylinder, forming a Taylor-Couterberg flow in the gap.

[0116] S3: When the rotor mechanism speed is low, the flow of the cooling medium in the gap is laminar. The reading M of the torque sensor is recorded, which is the rotational torque of the inner cylinder under this flow state.

[0117] S4: By changing the speed of the motor, the reading M of the torque sensor corresponding to different speeds is measured, thereby obtaining the rotational torque of the inner cylinder at different speeds;

[0118] S5: By changing the flow rate of the cooling medium through the inlet pipe, the reading M of the torque sensor corresponding to different axial flow rates is measured to obtain the rotational torque of the inner cylinder under different axial flow rates.

[0119] S6: By changing the axial length of the inner cylinder, the reading M of the torque sensor corresponding to different axial lengths is measured to obtain the rotational torque of the inner cylinder under different axial lengths.

[0120] In some possible implementations, such as Figure 3 As shown, the Taylor-Couterbury blade flow rotation torque measurement method also includes the following steps:

[0121] S7: Replace the inner cylinder with a different radius, and execute steps S3, S4 and S5 to obtain the rotational torque of the inner cylinder corresponding to different rotational speeds, axial flow rates and axial lengths under different radius ratios.

[0122] The Taylor-Couter-Poseidon blade flow rotation torque measurement method in this embodiment can accurately measure the rotation torque of the Taylor-Couter-Poseidon blade flow, providing a reference for motor cooling structure design, optimization, drive efficiency, and power generation efficiency improvement.

[0123] The above description, with reference to the accompanying drawings, illustrates a Taylor-Couterbury blade flow rotation torque measuring device and method according to embodiments of the present disclosure, which offers the following advantages:

[0124] This study enables the investigation of the rotational torque characteristics of Taylor-Couterbury blade flow under different rotational speeds, geometries, inlet flow rates, and axial lengths. It also allows for the development of related theoretical analyses and experimental research. The findings are of significant engineering and scientific importance for reducing oil churning losses between the stator and rotor of a motor and improving motor drive efficiency and power generation efficiency.

[0125] The basic principles of this disclosure have been described above with reference to specific embodiments. However, it should be noted that the advantages, benefits, and effects mentioned in this disclosure are merely examples and not limitations, and should not be considered as essential features of each embodiment of this disclosure. Furthermore, the specific details disclosed above are for illustrative and facilitative purposes only, and are not limitations. These details do not limit the scope of this disclosure to the necessity of employing the aforementioned specific details for implementation.

[0126] The block diagrams of devices, apparatuses, devices, and systems disclosed herein are merely illustrative examples and are not intended to require or imply that they must be connected, arranged, or configured in the manner shown in the block diagrams. As those skilled in the art will recognize, these devices, apparatuses, devices, and systems can be connected, arranged, and configured in any manner. Words such as “comprising,” “including,” “having,” etc., are open-ended terms meaning “including but not limited to,” and are used interchangeably with them. The terms “or” and “and” as used herein refer to the terms “and / or,” and are used interchangeably with them unless the context clearly indicates otherwise. The term “such as” as used herein refers to the phrase “such as but not limited to,” and is used interchangeably with it.

[0127] Additionally, as used herein, the “or” used in a list of items beginning with “at least one” indicates a separate list, such that a list of, for example, “at least one of A, B, or C” means A or B or C, or AB or AC or BC, or ABC (i.e., A and B and C). Furthermore, the word “exemplary” does not imply that the described example is preferred or better than other examples.

[0128] It should also be noted that in the systems and methods of this disclosure, the components or steps can be decomposed and / or recombined. These decompositions and / or recombinations should be considered as equivalent solutions to this disclosure.

[0129] Various changes, substitutions, and modifications can be made to the technology described herein without departing from the teachings defined by the appended claims. Furthermore, the scope of the claims of this disclosure is not limited to the specific aspects of the processes, machines, manufactures, events, means, methods, and actions described above. Currently existing or later-developed processes, machines, manufactures, events, means, methods, or actions that perform substantially the same function or achieve substantially the same result as the corresponding aspects described herein can be utilized. Therefore, the appended claims include such processes, machines, manufactures, events, means, methods, or actions within their scope.

[0130] The above description of the disclosed aspects is provided to enable any person skilled in the art to make or use this disclosure. Various modifications to these aspects will be readily apparent to those skilled in the art, and the general principles defined herein may be applied to other aspects without departing from the scope of this disclosure. Therefore, this disclosure is not intended to be limited to the aspects shown herein, but rather to be carried out within the widest scope consistent with the principles and novel features disclosed herein.

[0131] The above description has been given for purposes of illustration and description. Furthermore, this description is not intended to limit the embodiments of this disclosure to the forms disclosed herein. Although numerous exemplary aspects and embodiments have been discussed above, those skilled in the art will recognize certain variations, modifications, alterations, additions, and sub-combinations thereof.

Claims

1. A Taylor-Couterberg blade flow rotation torque measuring device, characterized in that, include: A stator mechanism, wherein a measuring chamber is provided inside the stator mechanism; A rotor mechanism is disposed in the measuring chamber and is rotatable relative to the stator mechanism. There is a gap (20) between the rotor mechanism and the stator mechanism, and a Taylor-Couterberg flow can be formed in the gap (20) by a cooling medium. A power transmission mechanism, wherein the power input end of the power transmission mechanism is connected to a motor; A torque measuring mechanism is provided in the measuring chamber, with its first end connected to the rotor mechanism and its second end connected to the power transmission mechanism. Among them, the motor drives the power transmission mechanism to rotate, the power transmission mechanism drives the torque measuring mechanism to rotate, the torque measuring mechanism drives the rotor mechanism to rotate, and the torque measuring mechanism measures the rotational torque change of the rotor mechanism, so as to obtain the rotational torque generated by the Taylor Cotepure blade flow in the gap (20); The stator mechanism includes: The first outer cylinder (3) has the rotor mechanism disposed inside the first outer cylinder (3); The rotor mechanism includes: The first drive shaft (5) has its second end connected to the torque measuring mechanism; Inner cylinder (6), the inner cylinder (6) is disposed on the first drive shaft (5), the first drive shaft (5) can drive the inner cylinder (6) to rotate, and there is a gap (20) between the outer circumference of the inner cylinder (6) and the inner circumference of the first outer cylinder (3). The inner cylinder (6) with different axial lengths can be replaced to change the axial length of the gap (20). A bushing (51) is provided on the first drive shaft (5) for axially limiting the inner cylinder (6); and / or, the inner cylinder (6) with different radii can be replaced to change the width of the gap (20). The torque measuring mechanism includes: A torque sensor (11) is used to measure the rotational torque change of the inner cylinder (6); A first coupling (12) is connected to the torque sensor (11) and the second end of the first drive shaft (5); The second coupling (13) connects the torque sensor (11) and the power transmission mechanism.

2. The Taylor-Couterberg blade flow rotation torque measuring device according to claim 1, characterized in that, The stator mechanism also includes: Front cover (1), the front cover (1) is disposed at the first end of the first outer cylinder (3), the front cover (1) is provided with a liquid inlet pipe (2) for inputting cooling medium; The second outer cylinder (9) is connected to the second end of the first outer cylinder (3). The cylinder wall of the second outer cylinder (9) is provided with a drain pipe (14) for outputting cooling medium. The torque measuring mechanism is located inside the second outer cylinder (9).

3. The Taylor-Couterberg blade flow rotation torque measuring device according to claim 2, characterized in that, The interior of the first outer cylinder (3) is provided with: A first bearing housing (31) is provided with a first bearing (32), the first bearing (32) supports the first end of the first transmission shaft (5), and the first bearing housing (31) is provided with a through hole through which a cooling medium can flow. The second bearing housing (33) is provided with a second bearing (34), which supports the second end of the first transmission shaft (5). The second bearing housing (33) is provided with a through hole through which a cooling medium can flow.

4. The Taylor-Couterberg blade flow rotation torque measuring device according to claim 2, characterized in that, The first coupling (12) and the second coupling (13) are flexible couplings.

5. The Taylor-Couterberg blade flow rotation torque measuring device according to claim 4, characterized in that, The power transmission mechanism includes: Magnetic torque transmitter (19), which is used to connect to a motor; The second drive shaft (15) has a first end connected to the second coupling (13) and a second end connected to the magnetic torque transmitter (19), which transmits the rotational torque to the torque measuring mechanism.

6. The Taylor-Couterberg blade flow rotation torque measuring device according to claim 5, characterized in that, The second outer cylinder (9) is provided with a third bearing seat (91), and a third bearing (92) is provided in the third bearing seat (91). The third bearing (92) supports the first end of the second transmission shaft (15). The third bearing seat (91) is a closed plate structure.

7. The Taylor-Couterberg blade flow rotation torque measuring device according to claim 5, characterized in that, The stator mechanism also includes: The third outer cylinder (16) has its first end connected to the second end of the second outer cylinder (9). The magnetic torque transmitter (19) is located at the second end of the third outer cylinder (16). The third outer cylinder (16) has a fourth bearing seat (161) inside it. The fourth bearing seat (161) has a fourth bearing (162) inside it. The fourth bearing (162) supports the second end of the second transmission shaft (15).

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