Taylor-Kutbosch flow rotation torque measuring device and test method thereof

Abstract

The present invention discloses a Taylor-Kutt-Poiseuille flow rotational torque measurement device and its testing method. The device includes a stator housing, a rotor structure, a torque measurement structure, and a signal transmission and power supply structure. The stator housing is sleeved on the rotor structure. The rotor structure includes a rotor shaft, an inlet section rotor, a test section rotor inner barrel, and an outlet section rotor. The torque measurement structure includes a lever arm and a force sensor. The signal transmission and power supply structure includes a battery end cap, a wireless signal transmitter, and a battery. The three-section rotor design minimizes the influence of the inlet and outlet section effects on the measurement of Taylor-Kutt-Poiseuille flow rotational torque law. At the same time, the rotor shaft rotational torque is only applied to the test section rotor inner barrel through the lever arm, reducing the influence of other additional rotational torques on the rotational torque measurement. The measurement results are more accurate, solving the problem that there are few existing Taylor-Kutt-Poiseuille flow rotational torque measurements and it is difficult to provide technical parameters for reducing motor cooling and oil stirring losses.

Description

Technical Field

[0001] The invention belongs to the field of rotational torque measurement, and in particular relates to a Taylor-Kutter-Poseyleaf flow rotational torque measurement device and a test method thereof. Background Art

[0002] Driven by the pursuit of smaller size and higher power, motor speeds have been rising all the way, from the early two to three thousand rpm to tens of thousands or even hundreds of thousands rpm. However, motor losses increase exponentially with speed. The high motor losses generate heat, causing the motor temperature to rise rapidly, requiring a well-designed motor cooling method. One of the most commonly used high-speed motor cooling methods is internal oil cooling.

[0003] However, using internal oil cooling to cool the motor rotor-stator gap presents new challenges to motor design. The flow losses caused by the cooling medium passing through the motor rotor-stator gap reduce the motor's output power. To achieve the required motor output power, the losses caused by the cooling medium flowing through the motor rotor-stator gap need to be considered. The flow of cooling medium in the gap between the high-speed rotating motor rotor and stator is called Taylor-Kutt-Poiseuille flow. Depending on the rotor speed and axial flow velocity, Taylor-Kutt-Poiseuille flow can produce a variety of flow patterns, with large flow losses, reducing the motor's power output. Qualitative and quantitative measurements are needed to determine the rotational torque patterns generated by the medium passing through the motor rotor-stator gap.

[0004] At the same time, rotational torque is affected by the coupling of many factors, such as rotor rotation speed, gap geometry, axial flow velocity, etc. Current research on the measurement of rotational torque mainly focuses on Taylor-Kutt flow without superimposed axial flow, and the measurement technology involved does not effectively eliminate the effect of additional rotational torque, resulting in insufficient measurement accuracy. At present, there is no high-precision Taylor-Kutt-Posesuet vane flow rotational torque measurement device in China. In order to study the rotational torque characteristics of Taylor-Kutt-Posesuet vane flow at different speeds, geometric structures, and inlet flow rates, relevant theoretical analysis and experimental research are needed. In addition, the measurement device can further conduct experimental research on the heat transfer characteristics of Taylor-Kutt-Posesuet vane flow. Research on the above content has important engineering and scientific significance for reducing the oil stirring loss in the rotor-stator gap of the motor and improving the power generation efficiency of the motor. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to overcome the shortcomings of the existing technology and provide a Taylor-Court-Posey flow rotation torque measurement device and a test method thereof. To solve the above technical problems, the basic concept of the technical solution adopted by the present invention is:

[0006] An object of the present invention is to provide a Taylor-Kutt-Poseyleaf flow rotational torque measurement device to solve the existing problems related to Taylor-Kutt-Poseyleaf flow rotational torque measurement and to minimize the influence of additional rotational torque on the measurement results. A Taylor-Kutt-Poiseuille flow rotational torque measuring device comprises a power transmission structure, a sealing structure, a rotor structure, a stator structure, a support structure, a torque measuring structure, and a signal transmitting and power supply structure; the power transmission structure comprises a magnetic coupling connecting a motor shaft and a load rotor shaft to transmit the driving motor torque; the sealing structure comprises an isolation cover and left and right end covers, the magnetic coupling converts the dynamic seal generated by the connection between the motor shaft and the load shaft into a static seal, and seals the fluid through the isolation cover; the rotor structure comprises a rotor arranged on the rotor shaft, and the rotor is divided into three sections; the stator structure comprises a stator housing, and a gap for Taylor-Kutt-Poiseuille flow is formed between the rotor and the stator housing; the support structure comprises a rotor shaft support bearing and a test section rotor inner cylinder support bearing; the torque measuring structure comprises a force arm arranged between the rotor shaft and the test section rotor inner cylinder and a force sensor arranged on the force arm; the signal transmitting and power supply structure is arranged at the rotor shaft end for transmitting force sensor signals and facilitating the removal and replacement of batteries.

[0007] Furthermore, the magnetic coupling includes an outer ring, an isolation cover, and an inner rotor. The outer ring is connected to the drive motor shaft, the inner rotor is connected to the rotor shaft, the isolation cover separates the outer ring and the inner rotor, and the torque of the drive motor shaft is transmitted through magnets arranged on the cylindrical surfaces of the outer ring and the inner rotor.

[0008] Furthermore, the sealing structure includes a magnetic coupling isolation cover on the liquid inlet side connected to a left end cover arranged on the stator housing and a right end cover on the liquid outlet side connected to the stator housing.

[0009] Furthermore, the rotor structure comprises three sections: an inlet section, a test section, and an outlet section. The inlet and outlet sections are fixed to the rotor shaft and axially positioned by locknuts. The test section rotor utilizes a hollow cylindrical inner barrel supported by bearings. Small gaps separate the three sections to minimize fluid leakage into the gaps between the rotors. The three-section rotor structure is designed to minimize the impact of inlet and outlet effects on torque measurement, allowing only the more regular torque of the intermediate section to be measured.

[0010] Furthermore, the stator structure includes a stator housing, which is provided with a liquid inlet and a liquid outlet. The fluid enters the left cavity from the liquid inlet and then enters the annular gap between the rotor structure and the stator housing, and then enters the right cavity and flows out through the liquid outlet provided on the stator housing.

[0011] Furthermore, the rotor shaft support bearings are arranged on both sides of the rotor shaft, the inner ring is connected to the rotor shaft, the outer ring is connected to the rotor shaft support bearing support, and the rotor shaft support bearing support is connected to the stator housing.

[0012] Furthermore, the test section rotor inner cylinder support bearings are arranged on both sides near the middle of the rotor shaft, the inner ring is connected to the rotor shaft, and the outer ring is connected to the test section rotor inner cylinder support bearing support.

[0013] Furthermore, the test section rotor inner cylinder support bearing support is provided with grate teeth, which cooperate with the inlet section rotor and the outlet section rotor to better reduce the leakage of fluid through the gap between the rotors.

[0014] Furthermore, the inner tube end cover of the test section rotor is designed to be a detachable structure, forming a cavity between the inlet section rotor and the outlet section rotor, which can accommodate standard sealing parts and self-designed sealing parts.

[0015] Furthermore, the force arm is arranged on the rotor shaft and the test section rotor inner cylinder, and is divided into two sections, each of which is L-shaped. The force sensor is arranged in the middle of the two sections of the force arm and connects the two sections of the force arm. The rotor shaft transmits the rotational torque to the test section rotor inner cylinder only through the force arm. The force sensor is used to measure the magnitude of the transmitted force, and a wireless signal transmitter is used to transmit the force measurement signal.

[0016] Furthermore, the wireless signal transmitter and battery are arranged at the end of the rotor shaft, and a battery end cover is provided to isolate the fluid to prevent the wireless signal transmitter and the battery from being inactivated by the fluid and to facilitate the disassembly and replacement of the battery; the signal connection line of the force sensor is passed through a hole punched on the rotor shaft and connected to the wireless signal transmitter arranged at the end of the shaft.

[0017] Another object of the present invention is to provide a method for testing the aforementioned Taylor-Kutt-Posey vane flow rotational torque measuring device to address the current lack of Taylor-Kutt-Posey vane flow rotational torque testing methods and to solve the problem that existing testing methods are unable to provide technical parameters for reducing motor cooling oil churning losses. The method comprises the following steps:

[0018] S1: The drive motor provides the rotor shaft with rotational power, and the magnetic coupling transmits the rotational torque of the drive motor shaft;

[0019] S2: When the rotor shaft rotates at low speed, the fluid flows into the inlet side cavity from the liquid inlet hole of the stator housing, flows into the outlet side cavity through the gap formed between the rotor and the stator housing, and then flows out through the liquid outlet hole of the stator housing, forming a Taylor-Kutbseugye flow in the rotor-stator gap;

[0020] S3: When the rotor shaft speed is low, the gap flow is laminar, and the force sensor reading F is recorded. The rotational torque under this flow state is T=F·L, where F is the force sensor reading and L is the radius at the force measurement point.

[0021] S4: By changing the speed of the driving motor, measuring the force sensor reading F corresponding to different speeds, thereby obtaining the rotational torque of the inner cylinder of the test section rotor at different speeds;

[0022] S5: By changing the flow rate of the fluid passing through the inlet and outlet holes, the force sensor reading F corresponding to different axial flow rates is measured, thereby obtaining the rotational torque of the inner cylinder of the test section rotor under different axial flow rates.

[0023] Furthermore, the method further includes step S6: replacing rotors of different radii, executing steps S3, S4 and S5, and obtaining the rotational torque of the inner cylinder of the test section rotor corresponding to different speeds and axial flow rates under different radius ratios; wherein the radii of the inlet section rotor, the outlet section rotor and the inner cylinder of the test section rotor can all be disassembled and replaced as needed.

[0024] After adopting the above technical solution, the present invention has the following beneficial effects compared with the prior art.

[0025] The present invention connects the drive motor shaft and the rotor shaft through a magnetic coupling, which can convert the dynamic seal required for contact torque transmission into a static seal, thereby simplifying the sealing structure design and preventing fluid from leaking to the outside; through the three-section rotor design, the influence of the inlet and outlet section effects on the measurement of the Taylor-Kutt-Posey flow rotational torque law is minimized as much as possible, and it is concluded that the rotational torque of the inner cylinder of the intermediate test section has regular changes; the test section rotor is supported by the test section rotor inner cylinder bearing, and the rotor shaft rotational torque is only applied to the test section rotor inner cylinder through the force arm, reducing the influence of other additional rotational torques such as bearing resistance torque, end face resistance torque, etc. on the rotational torque measurement, and the measurement result is more accurate; through the comb tooth structure designed on the test section rotor bearing support and the cavity design of the replaceable sealing structure, the leakage of fluid from the gap between the test section rotor end face and the inlet section rotor end face and the outlet section rotor end face is reduced, so that the fluid flows out through the rotor-stator gap.

[0026] The present invention can accurately test the rotational torque of Taylor-Kutt-Poiseuille flow under different rotor rotation speeds and different axial flow rates, providing a reference basis for the design and optimization of motor cooling structure and the improvement of motor power generation efficiency.

[0027] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The accompanying drawings are part of this application and are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention, but do not constitute an undue limitation of the present invention. Obviously, the drawings described below are only some embodiments. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without inventive effort. In the accompanying drawings:

[0029] Figure 1 2 is a schematic structural diagram of a Taylor-Kutbossler flow rotational torque measuring device according to an embodiment of the present invention;

[0030] Figure 2 Schematic diagram of the structure of the force sensor and the force arm according to an embodiment of the present invention.

[0031] In the figure: 1-outer ring, 2-isolation cover, 3-inner rotor, 4-locking nut, 5-left end cover, 6-bearing preload spring, 7-sleeve, 8-rotor shaft support bearing, 9-rotor shaft support bearing support, 10-locking nut, 11-rotor shaft, 12-stator housing, 13-inlet section rotor, 14-test section rotor inner cylinder end cover, 15-seal, 16-test section rotor inner cylinder support bearing support, 17-test section rotor inner cylinder support bearing, 18-lever, 19-force sensor, 20-test section rotor inner cylinder, 21-outlet section rotor, 22-battery end cover, 23-right end cover, 24-wireless signal transmitter and battery, 25-sleeve, 26-liquid inlet hole, 27-liquid outlet hole.

[0032] It should be noted that these drawings and textual descriptions are not intended to limit the conceptual scope of the present invention in any way, but rather to illustrate the concept of the present invention for those skilled in the art by referring to specific embodiments. DETAILED DESCRIPTION

[0033] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. The following embodiments are used to illustrate the present invention but are not used to limit the scope of the present invention.

[0034] In the description of the present invention, it should be noted that the terms "upper", "lower", "front", "back", "left", "right", "vertical", "inside", "outside", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the present invention.

[0035] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; and direct or indirect connections through an intermediary. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances. Example 1

[0036] like Figure 1-2 As shown, the Taylor-Kutbauer flow rotation torque measuring device described in this embodiment includes a stator structure, a rotor structure, a torque measuring structure, a signal transmission and power supply structure, a power transmission structure, a sealing structure, and a support structure. The stator structure is the stator housing 12, which is correspondingly a hollow cylindrical cylinder including a cylindrical liquid inlet hole 26 and a liquid outlet hole 27. That is, the liquid inlet hole 26 and the liquid outlet hole 27 are designed on both sides of the stator housing 12. The position and size of the liquid inlet hole 26 and the liquid outlet hole 27 can be determined according to actual conditions. The inside and outside of the stator housing 12 are both cylindrical surfaces. The rotor structure is preferably a solid perforated cylindrical inlet section rotor 13 and outlet section rotor 21 and a hollow test section rotor inner cylinder 20. The power transmission structure is preferably a cylindrical synchronous magnetic coupling, and the support structure includes a first support bearing group and a second support bearing group, preferably using angular contact ball bearings.

[0037] The rotor structure includes a rotor shaft 11, an inlet section rotor 13, a test section rotor inner tube 20, and an outlet section rotor 21. The rotor shaft is supported by a first bearing support group, with two first bearing support groups respectively arranged at its two ends. A fluid cavity is formed between the two first support bearing groups, and the liquid inlet and liquid outlet are connected to the fluid cavity. The inlet section rotor 13, the test section rotor inner tube 20, and the outlet section rotor 21 are all located in the fluid cavity. The rotor shaft 11 adopts a hollow shaft design with a channel inside. The purpose is to lead out the signal connection line of the force sensor 19 and connect it to the wireless signal transmitter and battery 24 in the signal transmission and power supply structure arranged at the shaft end. The inlet section rotor 13 and the outlet section rotor 21 are cylindrical, with an axial hole set in the middle to cooperate with the rotor shaft 11 and axial positioning is performed by the rotor shaft shoulder and the locking nut 10. The test section rotor inner cylinder 20 adopts a hollow design, with both inner and outer surfaces being coaxial cylindrical surfaces, forming a cavity between the rotor shaft 11 for placing the torque measurement structure. The test section rotor inner cylinder 20 is mounted on the outer wall of the rotor shaft 11 through two second support bearing groups.

[0038] The inlet-segment rotor 13, outlet-segment rotor 21, and test-segment rotor inner barrel 20 have the same outer diameter, slightly smaller than the inner diameter of the stator housing. These diameters can be machined to different sizes as needed. A rotor-stator gap is formed between the outer annular surfaces of the three rotors and the inner annular surface of the stator housing 12. A very small gap is left between the test-segment rotor inner barrel 20 and the inlet-segment rotor 13 and outlet-segment rotor 21 to prevent contact between the three rotors from affecting the measurement of the test-segment rotor inner barrel 20's rotational torque. Preferably, the gaps between the three rotors are as small as possible to prevent fluid leakage through the gaps between the rotors and maximize fluid flow through the rotor-stator gap.

[0039] The torque measurement structure is set in the cavity, and the torque measurement structure includes a force arm 18 and a force sensor 19. The force arm 18 is L-shaped, and one end of the L-shaped is set on the inner wall of the test section rotor inner cylinder 20, and the other end is connected to the rotor shaft 11 through the force sensor 19; the rotation torque measurement structure is as follows Figure 2 As shown, the lever arm 18 is divided into two sections: one located on the inner cylinder of the test section rotor, and the other on the rotor shaft. Both sections are L-shaped, with a force sensor 19 positioned between them. Rotating the rotor shaft causes the lever arm to squeeze the force sensor, causing deformation. Using the Wheatstone bridge principle, this deformation is converted into an electrical signal, which, after processing, can be used to measure the force applied at the point of application. In this example, a small S-shaped force sensor is used, which is compact and offers excellent linearity, repeatability, and measurement accuracy.

[0040] The signal transmission and power supply structure includes a battery end cap 22, a wireless signal transmitter and a battery 24. The battery end cap 22 is connected to the end of the rotor shaft 11 in a cover-type buckle manner to form a protective cavity. The wireless signal transmitter and the battery 24 are arranged in the protective cavity and are fixedly connected to the end of the rotor shaft 11. The connecting line of the force sensor 19 extends through the channel of the rotor shaft 11 and is connected to the wireless signal transmitter and the battery 24. The wireless signal transmitter and the battery 24 are arranged at the end of the rotor shaft and are sealed by the battery end cap 22 to prevent fluid from entering. The force sensor signal line enters the hollow rotor shaft through the hole on the rotor shaft and is connected to the wireless signal transmitter. The battery supplies power to the wireless signal transmitter and can be easily disassembled and replaced. The battery end cap 22 here adopts a transparent acrylic structure, which can better transmit the wireless signal.

[0041] The magnetic coupling comprises an outer ring 1, a cage 2, and an inner rotor 3. The inner rotor 3 is solidly mounted on one end of the rotor shaft 11. The outer ring 1 is buckled around the inner rotor 3 and connected to the drive motor shaft. The cage 2 is positioned between the outer ring 1 and the inner rotor 3 and connects to the end of the stator housing 12 via the left end cap 5, forming a sealed chamber within which the inner rotor 3 resides. The magnetic coupling transmits torque from the drive motor shaft to the rotor shaft. The left end of the outer ring 1 is hollow cylindrical, mating with the drive motor shaft. The connection is clamped, but not limited to this. The left end of the outer ring 1 transitions into a hollow cylinder with a larger radius, mating with the inner rotor 3. Magnets are evenly distributed on the inner annular surface of the outer ring 1 and the inner rotor 3. The inner rotor 3 is also hollow cylindrical, connecting to the rotor shaft 11. Magnets are also evenly distributed on the outer annular surface of the inner rotor 3. The outer ring 1 and the inner rotor 3 are separated by the cage 2.

[0042] The sealing structure is annular and includes a left end cover 5 and a right end cover 23. The left end cover 5 is connected to the stator housing 12, and the isolation cover 2 is connected to the left end cover 5 to achieve a leak-free static seal. During the transmission process, the isolation cover separates the external magnet and the internal magnet, and the magnetic lines of force pass through the isolation cover to transmit the power and movement of the external magnet to the inner magnet, thereby achieving contactless sealed transmission. The magnetic coupling adopts the principle of magnetic coupling to achieve the transmission of force and torque between the driving shaft and the driven shaft without direct contact, and can convert dynamic seals into static seals. One end of the rotor shaft 11 where the battery end cover 22 is installed is sealed by the right end cover 23. The right end cover 23 is connected to the stator housing 12 to form a sealed cavity. The battery end cover 22, the wireless signal transmitter and the battery 24 are all located in the sealed cavity. The right end cover 23 is directly connected to the stator housing 12 to achieve sealing.

[0043] The first support bearing assembly includes a rotor shaft support bearing 8 and a rotor shaft support bearing support 9. The rotor shaft support bearing 8 is sleeved on the rotor shaft 11, with its inner ring fixedly connected to the rotor shaft 11 and its outer ring fixedly connected to the rotor shaft support bearing support 9. The rotor shaft support bearing support 9 is connected to the inner wall of the stator housing 12. The inner ring of the rotor shaft support bearing 8 is connected to the rotor shaft 11, the outer ring of the rotor shaft support bearing 8 is connected to the inner annular surface of the rotor shaft support bearing support 9, and the outer annular surface of the rotor shaft support bearing support 9 is connected to the inner annular surface of the stator housing 12. The rotor shaft support bearing 8 is axially positioned by a locking nut 4 and a sleeve 7. Preferably, the inner ring surface of the rotor shaft support bearing support 9 is provided with a step that is clamped on the end surface of the rotor shaft support bearing 8. A bearing preload spring 6 is provided between the left end cover 5 and the first support bearing group. The bearing preload spring 6 is sleeved on the rotor shaft 11, and its two ends are respectively in contact with the left end cover 5 and the first support bearing group. The bearing preload spring 6 is in a compressed state, and the bearing preload spring 6 applies an axial preload force to ensure a certain axial movement of the rotor shaft support bearing support 9.

[0044] The second support bearing assembly includes a test section rotor inner barrel support bearing 17 and a test section rotor inner barrel support bearing support 16. The test section rotor inner barrel support bearing 17 is mounted on the rotor shaft 11. Its inner ring is fixedly connected to the rotor shaft 11, while its outer ring is connected to the test section rotor inner barrel support bearing support 16. The test section rotor inner barrel support bearing support 16 is connected to the inner wall of the test section rotor inner barrel 20. The inner ring of the test section rotor inner barrel support bearing 17 is connected to the rotor shaft 11, while its outer ring is connected to the test section rotor inner barrel support bearing support 16. Unlike conventional bearings, where the outer ring remains stationary, the outer ring of the test section rotor inner barrel support bearing 17 rotates at the same speed as the test section rotor inner barrel support bearing support. The entire test section rotor and its associated structures rotate at the same speed. The test section rotor inner barrel support bearing 17 provides only support. The torque applied to the test section rotor inner barrel 20 by the rotor shaft 11 is transmitted solely through the lever arm 18. This significantly reduces the additional drag torque caused by bearing rotation that affects rotational torque measurement.

[0045] Furthermore, to prevent fluid from leaking into the torque measurement cavity through the gaps between the rotors, a grate structure is designed on the test section rotor inner cylinder support bearing support 16. Specifically, grate teeth are provided on one radial end face of the test section rotor inner cylinder support bearing support 16, and the corresponding inlet section rotor 13 and outlet section rotor 21 are both equipped with offset grate teeth that mate with the grate teeth. A test section rotor inner cylinder end cap 14 is mounted on the outside of the test section rotor inner cylinder support bearing support 16. This end cap 14 is sleeved onto the rotor shaft 11 and is sealed to the test section rotor inner cylinder support bearing support 16. A cavity is formed between the test section rotor inner cylinder end cap 14 and the inlet section rotor 13 and outlet section rotor 21, within which a seal 15 is installed. The cavity formed by the grate teeth further reduces fluid leakage, and the installation of the seal 15 further reduces fluid leakage into the torque measurement structure cavity. The seal 15 is designed to be a detachable structure. A cavity is formed between the inlet section rotor 13, the test section rotor inner tube end cover 14 and the shaft sleeve 25 to place the seal. The seal 15 can be designed by itself or a standard seal kit can be selected. Preferably, a magnetic sealing structure is selected. Compared with the ordinary sealing structure, the main advantages of the magnetic end face seal are fewer structural elements, compactness, and easy installation. The contact load of the sealing interface can be designed to be smaller (only 25%~50% of the ordinary spring-loaded end face seal) and evenly distributed. At the same time, the additional rotational resistance torque brought by the sealing structure to the test section rotor rotation torque measurement can be reduced.

[0046] When conducting experiments using the device of the present invention, the torque transmission path is as follows: the torque output by the drive motor shaft is transmitted to the rotor shaft 11 through the magnetic coupling. The rotor shaft 11 transmits part of the torque to the inlet section rotor 13 and the outlet section rotor 21 through the pins. The rotor shaft 11 transmits the remaining torque to the test section rotor inner cylinder 20 through the lever arm 18, completing the drive of the rotor.

[0047] During the experiment, the fluid enters the cavity formed by the rotor shaft support bearing support 9 and the inlet section rotor 13 from the liquid inlet hole 26 of the stator housing 12. It then flows through the rotor-stator gap and enters the cavity formed by the outlet section rotor 21 and the rotor shaft support bearing support 9 before flowing out from the liquid outlet hole 27 of the stator housing 12. The inner annular surface of the stator housing 12 and the outer annular surface of the three-section rotor form a rotor-stator gap. The fluid flows within this gap to form a Taylor-Kutt-Poiseuille flow. A small gap size is preferably used for testing. The three-section rotor design minimizes the impact of the inlet and outlet section effects on the measurement of the Taylor-Kutt-Poiseuille flow rotational torque, resulting in a regular change in the rotational torque of the inner barrel of the intermediate test section. The test section rotor inner barrel bearing supports the test section rotor, and the rotor shaft rotational torque is applied to the test section rotor inner barrel only through the lever arm, reducing the impact of other additional rotational torques such as bearing resistance torque and end face resistance torque on the rotational torque measurement, and the measurement results are more accurate.

[0048] The fluid can be liquids such as water and alcohol. Preferably, the organic working fluid n-decane is used as the test liquid. During the experiment, the fluid will also enter the cavity at the inner rotor of the magnetic coupling through the rotor shaft support bearing 8, and the fluid will be sealed via the isolation cover 2. Similarly, the fluid will also enter the cavity between the battery end cover 22 and the stator housing 12 through the rotor shaft support bearing 8 at the outlet, and the fluid will be sealed via the right end cover 23. By connecting the drive motor shaft and the rotor shaft through a magnetic coupling, the dynamic seal required for contact torque transmission can be converted into a static seal, thereby simplifying the design of the sealing structure and avoiding leakage of the fluid to the outside world. At the same time, the comb structure designed on the test section rotor bearing support and the cavity design of the replaceable sealing structure reduce the leakage of the fluid from the gap between the test section rotor end face and the inlet section rotor end face and the outlet section rotor end face, so that the fluid flows out through the rotor-stator gap.

[0049] The Taylor-Kutt-Powell flow rotational torque test method of this embodiment is tested using the aforementioned Taylor-Kutt-Powell flow rotational torque measuring device. The method includes the following steps:

[0050] S1: The drive motor provides the rotor shaft with rotational power, and the magnetic coupling transmits the rotational torque of the drive motor shaft; Figure 1 Install the connection relationship of the various components of the measuring device, start the drive motor to make the rotor shaft rotate at a low speed;

[0051] S2: When the rotor shaft rotates at low speed, the fluid flows into the inlet side cavity from the liquid inlet hole of the stator housing, flows into the outlet side cavity through the gap formed between the rotor and the stator housing, and then flows out through the liquid outlet hole of the stator housing, forming a Taylor-Kutbseugye flow in the rotor-stator gap;

[0052] S3: When the rotor shaft speed is low, the gap flow is laminar, and the force sensor reading F is recorded. The rotational torque under this flow state is T=F·L, where F is the force sensor reading and L is the radius at the force measurement point.

[0053] S4: By changing the speed of the driving motor, measuring the force sensor reading F corresponding to different speeds, thereby obtaining the rotational torque of the inner cylinder of the test section rotor at different speeds;

[0054] S5: By changing the flow rate of the fluid passing through the inlet and outlet holes, the force sensor reading F corresponding to different axial flow rates is measured, thereby obtaining the rotational torque of the inner cylinder of the test section rotor under different axial flow rates.

[0055] S6: Replace rotors with different radii, execute steps S3, S4 and S5, and obtain the rotational torque of the inner cylinder of the test section rotor corresponding to different speeds and axial flow rates under different radius ratios; wherein the radii of the inlet section rotor, outlet section rotor and inner cylinder of the test section rotor can be disassembled and replaced as needed.

[0056] The precise test of the rotational torque of Taylor-Kutt-Poiseuille flow at different rotor rotation speeds and different axial flow rates can be carried out, providing a reference for the design and optimization of motor cooling structure and the improvement of motor power generation efficiency.

[0057] The above description is merely a preferred embodiment of the present invention and does not constitute any form of limitation to the present invention. Although the present invention has been disclosed as above in terms of a preferred embodiment, it is not intended to limit the present invention. Any technician familiar with this patent can make slight changes or modifications to equivalent embodiments using the above technical content without departing from the scope of the technical solution of the present invention. However, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention are still within the scope of the solution of the present invention.

Claims

1. A Taylor-Kutbosch flow rotation torque measuring device, characterized in that: It includes a stator housing (12), a rotor structure, a torque measurement structure, and a signal transmission and power supply structure; The stator housing (12) is sleeved outside the rotor structure, and the stator housing (12) is provided with a liquid inlet and a liquid outlet extending from the outside to the inner cavity; The rotor structure comprises a rotor shaft (11), an inlet section rotor (13), a test section rotor inner cylinder (20), and an outlet section rotor (21); both ends of the rotor shaft (11) are rotatably sleeved with first support bearing groups, and a fluid cavity is formed between the two first support bearing groups; the liquid inlet and the liquid outlet are communicated with the fluid cavity; the inlet section rotor (13), the test section rotor inner cylinder (20), and the outlet section rotor (21) are all located in the fluid cavity; the rotor shaft (11) is a hollow shaft with a channel therein; the inlet section rotor (13), the outlet section rotor (21) are 1) are all fixedly sleeved and mounted on the outer wall of the rotor shaft (11); the test section rotor inner cylinder (20) is sleeved and mounted on the outer wall of the rotor shaft (11) through two second support bearing groups; a sealed cavity is formed between the inner wall of the test section rotor inner cylinder (20), the inner walls of the two second support bearing groups, and the outer wall of the rotor shaft (11); the inlet section rotor (13), the test section rotor inner cylinder (20), and the outlet section rotor (21) are arranged in a line, with gaps between them; and a rotor-stator gap is formed between the outer annular surfaces of the three and the inner annular surface of the stator housing (12); The torque measurement structure is arranged in the cavity, and the torque measurement structure includes a force arm (18) and a force sensor (19). The force arm (18) is L-shaped, one section of the L-shaped structure is arranged on the inner wall of the test section rotor inner cylinder (20), and the other section is connected to the rotor shaft (11) through the force sensor (19); The signal transmission and power supply structure includes a battery end cover (22), a wireless signal transmitter and a battery (24); the battery end cover (22) is connected to the end of the rotor shaft (11) in a buckle-type manner to form a protective cavity; the wireless signal transmitter and the battery (24) are arranged in the protective cavity and fixedly connected to the end of the rotor shaft (11); the connecting line of the force sensor (19) extends through the channel of the rotor shaft (11) and is connected to the wireless signal transmitter and the battery (24).

2. The Taylor-Kutbosch flow rotation torque measuring device according to claim 1, characterized in that: The invention also includes a magnetic coupling, which includes an outer ring (1), an isolation cover (2), and an inner rotor (3). The inner rotor (3) and a solid sleeve are arranged on one end of the rotor shaft (11). The outer ring (1) is buckled on the outer periphery of the inner rotor (3) and is connected to the drive motor shaft. The isolation cover (2) is arranged between the outer ring (1) and the inner rotor (3) and is connected to the end of the stator housing (12) through the left end cover (5) to form a sealed cavity. The inner rotor (3) is located in the sealed cavity.

3. The Taylor-Kutbosch flow rotation torque measuring device according to claim 2, characterized in that: One end of the rotor shaft (11) on which the battery end cover (22) is mounted is connected by the right end cover (23) to form a sealed cavity, wherein the battery end cover (22), the wireless signal transmitter and the battery (24) are all located in the sealed cavity.

4. The Taylor-Kutbseule flow rotation torque measuring device according to claim 2, characterized in that: A bearing preload spring (6) is provided between the left end cover (5) and the first support bearing group. The bearing preload spring (6) is sleeved on the rotor shaft (11), with its two ends respectively contacting the left end cover (5) and the first support bearing group. The bearing preload spring (6) is in a compressed state.

5. The Taylor-Kutbseule flow rotation torque measuring device according to claim 1, characterized in that: The first support bearing group comprises a rotor shaft support bearing (8) and a rotor shaft support bearing support (9); the rotor shaft support bearing (8) is sleeved on the rotor shaft (11); the inner ring is fixedly connected to the rotor shaft (11); the outer ring is fixedly connected to the rotor shaft support bearing support (9); and the rotor shaft support bearing support (9) is connected to the inner wall of the stator housing (12).

6. The Taylor-Kutbseule flow rotation torque measuring device according to claim 1, characterized in that: The second support bearing group comprises a test section rotor inner tube support bearing (17) and a test section rotor inner tube support bearing support (16); the test section rotor inner tube support bearing (17) is sleeved on the rotor shaft (11); the inner ring is fixedly connected to the rotor shaft (11); the outer ring is connected to the test section rotor inner tube support bearing support (16); and the test section rotor inner tube support bearing support (16) is connected to the inner wall of the test section rotor inner tube (20).

7. The Taylor-Kutbseule flow rotation torque measuring device according to claim 6, characterized in that: A radial end surface of one side of the test section rotor inner cylinder supporting bearing support (16) is provided with grate teeth, and the corresponding inlet section rotor (13) and outlet section rotor (21) are both provided with offset grate teeth that cooperate with the grate teeth.

8. The Taylor-Kutbosch flow rotation torque measuring device according to claim 6, characterized in that: A test section rotor inner tube end cover (14) is installed on the outer side of the test section rotor inner tube support bearing support (16). The test section rotor inner tube end cover (14) is sleeved on the rotor shaft (11) and is sealedly connected to the test section rotor inner tube support bearing support (16). A cavity is formed between the test section rotor inner tube end cover (14) and the inlet section rotor (13) and the outlet section rotor (21), and a sealing member (15) is installed in the cavity.

9. A method for performing Taylor-Kutter-Poiseuille flow rotation torque testing using the apparatus according to any one of claims 1 to 8, characterized in that: The following steps are involved: S1: The drive motor provides rotational power, and the magnetic coupling transmits the rotational torque of the drive motor shaft to the rotor shaft (11); S2: When the rotor shaft (11) rotates at a low speed, the fluid flows into the inlet side cavity from the liquid inlet hole of the stator housing, flows into the outlet side cavity through the gap formed between the rotor and the stator housing (12), and then flows out through the liquid outlet hole of the stator housing, forming a Taylor-Kutbauer flow in the rotor-stator gap; S3: When the rotor shaft (11) rotates at a low speed, the gap flow is laminar, and the force sensor reading F is recorded. The rotational torque under this flow state is T=F·L, where F is the force sensor reading and L is the radius at the force measuring point. S4: By changing the speed of the driving motor, measuring the force sensor reading F corresponding to different speeds, and obtaining the rotational torque of the inner cylinder of the test section rotor at different speeds; S5: By changing the flow rate of the fluid passing through the inlet and outlet holes, measuring the force sensor reading F corresponding to different axial flow rates, the rotational torque of the inner barrel of the test section rotor under different axial flow rates is obtained.

10. The method for testing the rotational torque of a Taylor-Kutter-Poiseuille flow according to claim 9, wherein: The step S6 is also included: Replace the rotor with a different radius and execute steps S3, S4 and S5 to obtain the rotational torque of the inner cylinder of the test section rotor corresponding to different speeds and axial flow rates at different radius ratios.

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