Non-newtonian fluid heat measurement calculation method and model

Abstract

The application relates to a non-Newton fluid heat measurement calculation method and model, which comprises a rotating inner rotor head and a fixed cylinder; a fluid to be measured is stored in the cylinder; the inner rotor head is arranged to rotate in the cylinder; a torque sensor and a rotating speed sensor are connected to the inner rotor head; the application has the advantages of reasonable design, compact structure and convenient use.

Description

Technical Field

[0001] This invention relates to a method and model for measuring and calculating the heat of non-Newtonian fluids. Background Technology

[0002] Fluid viscosity is the property of a fluid to impede the relative sliding of its particles. Viscosity: a measure of the stickiness of a fluid. The viscosity of the same fluid changes with temperature and pressure. Generally, as temperature increases, the viscosity of liquids decreases, while the viscosity of gases increases.

[0003] Non-Newtonian fluids are fluids in which the shear stress and shear deformation rate do not satisfy a linear relationship, such as grease, paint, toothpaste, molten fluids, and mud.

[0004] Currently, there is no reasonable calculation and measurement method for non-Newtonian fluids, making accurate measurement impossible and resulting in severe damage to heat flow.

[0005] This is used because momentum exchange occurs between fluids with different flow velocities, thus generating internal friction at the contact surface of different flow layers within the fluid, commonly known as viscous force.

[0006] For laminar flow of Newtonian fluids, Newton's law of internal friction applies. However, for turbulent or non-Newtonian fluids (e.g., paint, mud, molten fluids), the law of internal friction does not apply. Specialized measurements are required. Currently, there are no methods for measuring the aforementioned molten or high-viscosity fluids.

[0007] This invention proposes a completely new solution for existing fluid dynamics. Summary of the Invention

[0008] In general, the technical problem to be solved by this invention is to provide a method and model for measuring and calculating the heat of non-Newtonian fluids.

[0009] To solve the above problems, the technical solution adopted by the present invention is as follows: A non-Newtonian fluid heat measurement model includes an upper frame, an intermediate frame, and a lower frame arranged from top to bottom. A heating chamber with a detection cavity is provided in the intermediate body section; A measuring main component is installed in the inner cavity of the detection chamber; The main measuring component includes a cylindrical body that is either fixed or raised. A rotating inner rotor head is provided inside the cylinder; The fluid to be measured is stored in a cylinder; The inner rotor head is set to rotate within the cylinder; The inner rotor head is connected to a torque sensor and a speed sensor.

[0010] As a further improvement to the above technical solution: The lower frame is equipped with a heater and a lifting cylinder.

[0011] The heating chamber has a sealed baffle door; the lower end of the baffle door is connected to the lifting cylinder. The heating chamber is sealed and explosion-proof. The heater is connected to the heating chamber.

[0012] The side walls of the heating chamber are equipped with a double layer; A top inner cavity is provided at the top of the upper frame; a rotary motor unit is provided in the top inner cavity.

[0013] The rotating motor unit is connected to the inner rotor head via a coupling unit for transmission. A camera is installed in the top cavity; A side-heated serpentine path is provided in the interlayer; The heating chamber is equipped with an external circulation channel and a venting disc.

[0014] An air guide is installed above the top of the heating chamber.

[0015] The air guide section has a top inner cavity at the output end.

[0016] To measure the parameters of non-Newtonian fluids, a non-Newtonian fluid internal friction parameter measuring assembly includes a rotating inner rotor head and a fixedly mounted cylinder. The fluid to be measured is stored in a cylinder; The inner rotor head is set to rotate within the cylinder; The inner rotor head is connected to a torque sensor and a speed sensor.

[0017] As a further improvement to the above technical solution: To achieve the supporting connection, the inner rotor head is equipped with an upper support body; an upper cross frame is set on the upper support body, and the inner rotor head is set on the upper cross frame.

[0018] A carrier section is provided below the inner rotor head; The carrier section includes an electric cylinder mounting base plate; A servo electric cylinder is installed on the base plate of the electric cylinder; The upper end of the servo electric cylinder is connected to a rotor fixing block via an electric cylinder connecting flange; A heat insulation plate for the electric cylinder flange is installed between the electric cylinder connecting flange and the rotor fixing block; A cylindrical guide frame is connected to the rotor fixing block; a guide copper sleeve is provided on the cylindrical guide frame; The guide copper sleeve is raised and lowered on the column of the upper support body; A fixing block receiving cavity is provided in the rotor fixing block, and a cylindrical heat insulation sleeve is provided in the fixing block receiving cavity; To achieve heat insulation, a cylindrical sleeve is installed inside the cylinder.

[0019] For easy assembly and disassembly, the cylinder is connected to the rotor fixing block by manually tightening screws.

[0020] The cylinder includes a lower cylinder body that is sealed at the bottom; an upper cylinder body is provided at the upper end of the lower cylinder body; One side of the rotor fixing block is provided with a positive notch that communicates with the fixing block receiving cavity; A lower rotor fixing block is provided at the positive notch; A fixing block cover plate is connected to the lower rotor fixing block by a pin bolt and a manual locking nut; A heat insulation sleeve for the heating pipe is installed on the base plate of the electric cylinder; Side openings communicating with the receiving cavity of the fixing block are provided on both sides of the rotor fixing block; An air duct section communicating with the side opening is provided on the cylindrical guide frame.

[0021] A temperature sensor with a spring body is installed in the lower rotor fixing block.

[0022] A force sensor is installed between the electric cylinder connecting flange and the rotor fixing block; the servo electric cylinder is equipped with a displacement sensor. Measuring holes are distributed on the cylinder; The temperature sensor is inserted into the measuring hole and comes into contact with the cylinder.

[0023] The lower end of the air duct is connected to a guide pipe that passes through the heat insulation sleeve of the heating pipe.

[0024] A method for measuring internal friction parameters of a non-Newtonian fluid, using the aforementioned measuring components; the measurement method performs the following steps; First, the fluid to be tested is placed in the cylinder; under the guidance of the column of the upper support body, the servo electric cylinder drives the rotor fixing block to rise, so that the inner rotor head enters the inner cavity of the cylinder; Next, start the inner rotor head to rotate and perform measurements.

[0025] As a further improvement to the above technical solution: Hot air enters the rotor fixing block through the guide pipe and air duct on one side, and the temperature of the fluid to be tested is adjusted by the temperature change of the rotor fixing block.

[0026] Start the servo electric cylinder to descend to the set displacement and take a measurement.

[0027] This invention enables the measurement of internal friction parameters of non-Newtonian fluids, including viscosity coefficients, and can be performed under static tension or dynamic viscosity conditions. The invention is rationally designed, low-cost, robust, durable, safe, reliable, simple to operate, time-saving, labor-saving, cost-effective, compact, and easy to use.

[0028] This invention integrates the lower frame, middle frame, and upper frame into a single unit. Testing is conducted via a heated chamber. During testing, heating achieves high-pressure sealing. A lifting cylinder controls the opening and closing of the baffle door, ensuring a sealed heating chamber and preventing injury. An air guide provides temperature insulation. The top inner cavity houses the rotary motor and coupling. Heat insulation components are installed in each part. Measurements are taken within the inner cavity, and the main measuring component completes the measurement. A side-heated serpentine system provides interlayer insulation, preventing heat exchange and reducing heat loss. An external circulation channel monitors temperature, and a pressure relief diaphragm provides safety protection, preventing overheating and explosion.

[0029] By cleverly improving existing calculation methods, the performance measurement of molten fluid was realized. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the guide copper sleeve structure of the present invention.

[0031] Figure 2 This is a schematic diagram of the temperature sensor structure of the present invention.

[0032] Figure 3 This is a schematic diagram of the rotor fixing block structure of the present invention.

[0033] Figure 4 This is a schematic diagram of the upper support structure of the present invention.

[0034] Figure 5 This is a schematic diagram of the upper half of the cylinder of the present invention.

[0035] Figure 6 This is a schematic diagram of the rotor fixing block structure of the present invention.

[0036] Figure 7 This is a schematic diagram of the heating box structure of the present invention.

[0037] Figure 8 This is a schematic diagram of the upper support structure of the present invention.

[0038] Figure 9 This is a schematic diagram of the external circulation channel structure of the present invention.

[0039] Figure 10 This is a schematic diagram of the structure of the explosion relief disc of the present invention.

[0040] Figure 11This is a schematic diagram of the internal rotor head structure of the present invention.

[0041] The components include: 1. Lower frame; 2. Middle frame; 3. Upper frame; 4. Heating box; 5. Lifting cylinder; 6. Baffle door; 7. Air guide; 8. Top inner cavity; 9. Rotary motor; 10. Coupling; 11. Detection inner cavity; 12. Measuring main body; 14. Side heating snake path; 15. External circulation channel; 16. Explosion relief disc; 101. Upper support frame; 102. Upper cross frame; 103. Inner rotor head; 104. Carrier; 108. Rotor fixing block; 109. Fixing block receiving cavity; 110. Upper half of the cylinder; 111. Lower half of the cylinder. 112. Lower rotor fixing block; 113. Electric cylinder fixing base plate; 114. Fixing block cover plate; 115. Electric cylinder connecting flange; 116. Cylinder guide frame; 117. Cylinder heat insulation sleeve; 118. Pin bolt; 119. Heating pipe heat insulation sleeve; 120. Servo electric cylinder; 121. Guide copper sleeve; 122. Temperature sensor; 123. Guide pipe; 124. Manual locking screw; 125. Manual locking nut; 126. Spring body; 127. Electric cylinder flange heat insulation plate; 128. Air duct section; 129. Side opening section; 130. Front notch section. Detailed Implementation

[0042] like Figure 1-11 As shown, the non-Newtonian fluid internal friction parameter measuring assembly of this embodiment includes a rotating inner rotor head 103 and a fixedly installed cylinder. The cylinder contains the fluid to be measured; it can be a normal solid, a material in a high-temperature molten state, or a material with very high viscosity.

[0043] The inner rotor head 103 is rotated within the cylinder; The inner rotor head 103 is connected to a torque sensor and a speed sensor for data acquisition.

[0044] For specific details, the inner rotor head 103 is equipped with an upper support body 101; an upper horizontal frame 102 is provided on the upper support body 101, and the inner rotor head 103 is provided on the upper horizontal frame 102.

[0045] A carrier portion 104 is provided below the inner rotor head 103; The carrier part 104 includes an electric cylinder fixing base plate 113; A servo electric cylinder 120 is installed on the electric cylinder mounting base plate 113; The upper end of the servo electric cylinder 120 is connected to a rotor fixing block 108 via an electric cylinder connecting flange 115. A heat insulation plate 127 for the electric cylinder flange is provided between the electric cylinder connecting flange 115 and the rotor fixing block 108. A cylindrical guide frame 116 is connected to the rotor fixing block 108; a guide copper sleeve 121 is provided on the cylindrical guide frame 116; The guide copper sleeve 121 is raised and lowered on the column of the upper support body 101; A fixing block receiving cavity 109 is provided in the rotor fixing block 108, and a cylindrical heat insulation sleeve 117 is provided in the fixing block receiving cavity 109. The cylinder is installed in the cylinder insulation sleeve 117.

[0046] The cylinder is connected to the rotor fixing block 108 by a manual locking screw 124.

[0047] The cylinder includes a lower cylinder half 111 sealed at the lower end; an upper cylinder half 110 is provided at the upper end of the lower cylinder half 111. The rotor fixing block 108 has a notch 130 on one side that communicates with the fixing block receiving cavity 109; A lower rotor fixing block 112 is provided in the positive notch 130; A fixing block cover plate 114 is connected to the lower rotor fixing block 112 by a pin bolt 118 and a manual locking nut 125; A heating pipe insulation sleeve 119 is provided on the electric cylinder fixing base plate 113; Side openings 129 communicating with the fixing block receiving cavity 109 are provided on both sides of the rotor fixing block 108; An air duct 128 communicating with the side opening 129 is provided on the cylindrical guide frame 116.

[0048] A temperature sensor 122 with a spring body 126 is provided on the lower rotor fixing block 112.

[0049] Measuring holes are distributed on the cylinder; The temperature sensor 122 is used to insert into the measuring hole and contact the cylinder.

[0050] The lower end of the air duct section 128 is connected to a guide pipe 123 that passes through the heat insulation sleeve 119 of the heating pipe.

[0051] The method for measuring the internal friction parameters of non-Newtonian fluids in this embodiment utilizes the aforementioned measuring components; the measurement method performs the following steps; First, the fluid to be tested is stored in the cylinder; under the guidance of the column of the upper support body 101, the guide copper sleeve 121 is driven by the servo electric cylinder 120 to rise the rotor fixing block 108, so that the inner rotor head 103 enters the inner cavity of the cylinder. Next, start the inner rotor head 103 to rotate and perform measurements.

[0052] Hot air enters the rotor fixing block 108 through the guide pipe 123 and the air duct 128 on one side, and the temperature of the fluid to be tested is adjusted by the temperature change of the rotor fixing block 108.

[0053] The servo electric cylinder 120 is started to perform lifting and lowering displacement and to perform traction measurement, which can be dynamic or static traction.

[0054] This invention achieves heating through the air duct 128, with one inlet and one outlet. Parameter measurement is achieved through rotation. The upper half 110 and lower half 111 of the cylinder are designed as separate units, preferably connected by bolts for easy cleaning and replacement. An inner spiral sleeve can be installed in the lower half 111 to allow for multi-condition testing. Data acquisition is achieved through sensors.

[0055] like Figure 1-10 Obtaining cut-related parameters: Before the experiment, the rotor size was first determined, and the heat was calculated based on the rotor configuration and material weight. The heat of the flowing material is obtained using the classic heat-temperature calculation formula. (1); Represents heat, unit: J; Specific heat capacity (an input value for the material), unit J / (kg·K); For the mass of the flow material, rotor, and cylinder (input values ​​for the material); These are the temperature changes of the material flow, rotor, and cylinder (test values ​​for the material).

[0056] During the material flow test, shear heat generation will cause the temperature of surrounding components to rise. The heat-absorbing components are: rotor, cylinder, material flow and air medium. The cylinder is wrapped with thermal insulation polytetrafluoroethylene, so heat loss here is negligible; the rotor and coupling are insulated from each other by thermal insulation material, so heat loss here is negligible; the contact between the material and the air medium is in the pressure-building area, and the contact area is small, so heat loss here is negligible. Therefore, during the shear test, the heat generated by the temperature rise of the flowing material is calculated from three factors: the cylinder, the rotor, and the flowing material itself, as shown in the following formula. (2); During the material flow test, the material is divided into four zones from bottom to top. The first zone at the bottom includes the contact cylinder bottom, and the fourth zone is exposed.

[0057] Temperature changes are extracted by four sets of sensors, with the bottom three sets corresponding to the rotor shearing region and the top set corresponding to the pressure build-up region.

[0058] This calculation uses a 2mm shear gap as an example. At this gap, 15g of flow material fills the shear gap but not the pressure-building area. Figure 1 As shown.

[0059] (3) Similarly, calculate the heat of the material flow and the rotor in the sensor area respectively: (4) (5) These are the specific heat capacities of the cylinder, rotor, and flow material, respectively; general values. These are the densities of the cylinder, rotor, and flow material, respectively; common values. These are the volumes of the cylinder, rotor, and material flow in the first region, respectively, which are directly output from the 3D model based on the actual design. The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature measured by the sensor in the first region.

[0060]

[0061] The rotor is made of steel, specifically 38CrMoAl-A (electroplated hard chrome). The rotor's specific heat as a function of temperature can be obtained (here, it can be considered a constant value; the rotor and cylinder are both metallic materials, and the temperature range is from room temperature to 150°C). o Within region C, the specific heat capacity changes very little. The mass of the material in this region is calculated by volume × density. The specific heat capacity of the molten material is a function of temperature and time, obtained experimentally. The filler material of the molten material is calculated.

[0062]

[0063] Calculate the heat of each component in the four sensor areas separately:

[0064] These are the specific heat capacities of the cylinder, rotor, and flow material, respectively; general values. These are the densities of the cylinder, rotor, and flow material, respectively, and are general values.

[0065] These are the volumes of the cylinder, rotor, and material flow in the second region, respectively, which are directly output from the 3D model based on the actual design.

[0066] The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature measured by the sensor in the second region.

[0067]

[0068] These are the specific heat capacities of the cylinder, rotor, and flow material, respectively; general values. These are the densities of the cylinder, rotor, and flow material, respectively, and are general values.

[0069] These represent the volumes of the cylinder, rotor, and material flow within the third region, respectively, which are directly output from the 3D model based on the actual design. The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature measured by the sensor in the third region.

[0070]

[0071]

[0072] These are the specific heat capacities of the cylinder, rotor, and flow material, respectively; general values. These are the densities of the cylinder, rotor, and flow material, respectively, and are general values.

[0073] These represent the volumes of the cylinder, rotor, and material flow within the fourth region, respectively. These volumes are directly output from the 3D model based on the actual design. The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature measured by the sensor in the fourth region.

[0074] The total heat is the sum of the heat from the four zones: (6)

[0075] The coaxial cylindrical rheometer fixture consists of a cylinder and an inner rotor head, with the sample filled in the gap between the cylinder and the inner cylinder. The flow field inside the cylinder is non-uniform, varying along the radial direction. When the gap between the inner cylinders is very small, the flow field can be approximated as uniform, thus the sample flow can be considered as simple shear flow. The working principle of the coaxial cylindrical rheometer is shown in Figure 1. The radius of the inner rotor head is... The radius of the cylinder is The inner rotor head moves at an angular velocity Rotate the cylinder and adopt a Cartesian coordinate system, aligning the z-axis with the cylinder's rotation axis, to obtain: (6) Its boundary conditions are: (7) (8) (9) (10) Substituting the boundary conditions into formula (6) yields the tangential velocity at a fluid radius of r. for: (11) The velocity gradient is: (12) According to the definition of a generalized Newtonian fluid, the distribution of shear stress... It can be represented as (13) The torque required for the inner rotor head to rotate is (14) In the formula, L represents the height of the liquid immersed in the cylinder. The viscosity can be expressed as follows by modifying the above formula: (15) Generally, during measurement, the inner rotor head is kept fixed while the cylinder rotates. This is because, at low rotational speeds, the fixed cylinder and rotating inner rotor head generate Taylor eddies, which can significantly affect the accuracy of the measurement results. Coaxial cylindrical rheometers are suitable for measuring fluids with low to medium viscosity, but not for measuring high-molecular-weight fluids or suspensions containing large molecules.

[0076] Let the motor torque be Melectric. If the torque from the motor to the reducer increases by 100 times, the torque from the reducer to the rotor, Mrotation, decreases by 40%. The motor torque is: (16) When the gap is 0.1: Shear stress Range: 10 3 -10 6 pa Shear stress 10 3 Pa, The rotational speed is n = 50 r / min = 0.83 r / s, kR = 2.05 cm, R = 1.95 cm, k = 1.05

[0077] angular velocity It is 5.2124 rad / s Substitute (13)

[0078] achievable =9.60 Pa / s Shear stress 10 6 Pa time Similarly, we can obtain =9604.51 Pa / s Viscosity range: 9.60-9604.51 Pa / s Rotor height 6 cm = 0.06 m Substitute into formula (14) when When =9.60 Pa / s, =4×3.14×9.60×0.06×5.2124×0.0195×0.0195×10.51 The torque is M = 0.15 N / m Similarly, when When the torque is 9604.51 Pa / s, the torque M is 150.72 N / m. Internal rotor head rotation torque range: 0.15-150.72 N / m According to the formula shear rate = shear stress / viscosity, we can obtain... The shear rate was 104.12 s. -1 The formula for calculating the motor torque is obtained by substituting the motor torque into equation (16). The motor torque is 0.002-2.51 N / m. When the gap is 0.2 Shear stress Range: 10 3 -10 6 pa Shear stress 10 3 Pa, The rotational speed is n = 50 r / min = 0.83 r / s, kR = 2.05 cm, R = 1.85 cm, k = 1.10.

[0079] angular velocity It is 5.2124 rad / s Substituting (13) yields =19.78 Pa / s Shear stress 106 Pa time Similarly, we can obtain =19780.84 Pa / s Viscosity range: 19.78-19780.84 Pa / s Rotor height 4 cm = 0.04 m Substitute into formula (9) when When the pressure is 19.78 Pa / s, the torque is M = 0.10 N / m. when When the torque is 19780.84 Pa / s, the torque M is 95.52 N / m. Internal rotor head rotation torque range: 0.10-95.52 N / m Based on the formula shear rate = shear stress / viscosity, we can obtain... The shear rate was 50.55 s⁻¹. -1 The formula for calculating the motor torque is obtained by substituting the motor torque into equation (11). The motor torque is 0.001-1.59 N / m. When the gap is 0.3 Shear stress Range: 10 3 -10 6 pa Shear stress 10 3 Pa, The rotational speed is n = 50 r / min = 0.83 r / s, kR = 2.05 cm, R = 1.75 cm, and k = 1.17.

[0080] angular velocity It is 5.2124 rad / s Substituting (13) yields =30.67 Pa / s Shear stress 10 6 Pa time Similarly, we can obtain =30673.30 Pa / s Viscosity range: 30.67-30673.30 Pa / s Rotor height 2.75 cm = 0.0275 m Substitute into formula (14) when When the pressure is 30.67 Pa / s, the torque M is 0.06 N / m. when When the pressure is 30673.30 Pa / s, the torque is M = 62.34 N / m. Internal rotor head rotation torque range: 0.06-62.34 N / m According to the formula shear rate = shear stress / viscosity, we can obtain... The shear rate was 32.60 s⁻¹. -1 The formula for calculating the motor torque is obtained by substituting the motor torque into equation (16). The motor torque is 0.001-1.039 N / m. When the height is 4.5 cm and the gap is 0.15 cm Shear stress Range: 10 3 -10 6 pa Shear stress 10 3 Pa, The rotational speed is n = 50 r / min = 0.83 r / s, kR = 2.26 cm, R = 2.11 cm, and k = 1.07.

[0081] angular velocity It is 5.2124 rad / s Substituting (13) yields =13.20 Pa / s Shear stress 10 6 Pa time Similarly, we can obtain =13201.58 Pa / s Viscosity range: 13.20-13201.58 Pa / s Rotor height 4.5 cm = 0.045 m Substitute into formula (14) when When the pressure is 13.20 Pa / s, the torque is M = 0.13 N / m. when When the torque is 13201.58 Pa / s, the torque M is 134.91 N / m. Internal rotor head rotation torque range: 0.13-134.91 N / m According to the formula shear rate = shear stress / viscosity, we can obtain... The shear rate was 75.74 s⁻¹. -1 The formula for calculating the motor torque is obtained by substituting the motor torque into equation (16). The motor torque ranges from 0.002 to 2.249 N / m. When the height is 5 cm and the gap is 0.15 cm Shear stress Range: 10 3 -10 6 pa Shear stress 10 3 Pa, The rotational speed is n = 50 r / min = 0.83 r / s, kR = 2.13 cm, R = 1.98 cm, and k = 1.07.

[0082] angular velocity It is 5.2124 rad / s Substituting (13) yields =14.04 Pa / s Shear stress 10 6 Pa time Similarly, we can obtain =14041.04 Pa / s Viscosity range 14.04-14041.04 Pa / s Rotor height 5 cm = 0.05 m Substitute into formula (14) when When the torque is 14.04 Pa / s, the torque M is 0.13 N / m. when When the torque is 14041.04 Pa / s, the torque M is 132.60 N / m. Internal rotor head rotation torque range: 0.13-132.60 N / m Based on the formula shear rate = shear stress / viscosity, we can obtain... The shear rate was 71.21 s⁻¹. -1 The formula for calculating the motor torque is obtained by substituting the motor torque into equation (16). The motor torque is 0.002-2.210 N / m. Similarly, when h=5.5 and the gap is 0.1, the shear stress is calculated as follows: R1=2.42 and R2=2.52. Range: 10 3 -10 6 Substituting pa into (13) yields The range is 7.77-7773.58 Pa / s. Substituting this into formula (14), we get the torque range M = 0.21-210.72 N / m. According to the formula shear rate = shear stress / viscosity, the shear rate is 128.64 s⁻¹. -1 The motor torque can be calculated by substituting the motor torque into formula (16). The motor torque is 0.003-3.512 N / m.

[0083] Similarly, when h=5.5 and the gap is 0.15, the shear stress is calculated as follows: R1=1.85 and R2=2. Range: 10 3 -10 6 Substituting pa into (13) yields The range is 14.99-14994.86 Pa / s. Substituting this into formula (14), we get the torque range M = 0.12-127.99 N / m. According to the formula shear rate = shear stress / viscosity, the shear rate is 66.69 s⁻¹. -1 The motor torque can be calculated by substituting the motor torque into formula (16). The motor torque is 0.002-2.133 N / m.

[0084] Similarly, when h=6 and the gap is 0.1, the shear stress is calculated as follows: R1=2.30, R2=2.40. Range: 10 3 -10 6 Substituting pa into (13) yields The range is 8.17-8171.23 Pa / s. Substituting this into formula (14), we get the torque range M = 0.20-208.09 N / m. According to the formula shear rate = shear stress / viscosity, the shear rate is 122.38 s⁻¹. -1 The motor torque can be calculated by substituting the motor torque into formula (16). The motor torque is 0.003-3.468 N / m.

[0085] Similarly, when h=6 and the gap is 0.15, the shear stress is calculated as follows: R1=1.74, R2=1.89. Range: 10 3 -10 6 Substituting pa into (13) yields The range is 15.91-15909.67 Pa / s. Substituting into formula (14), we get the torque range M=0.12-124.12 N / m. According to the formula shear rate = shear stress / viscosity, the shear rate is 62.85 s. -1 The motor torque can be calculated by substituting the motor torque into formula (16). The motor torque is 0.002-2.068 N / m.

[0086] The present invention has been described in detail for the purpose of making the disclosure clearer, and the prior art will not be listed in detail.

[0087] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. It is obvious to those skilled in the art that multiple technical solutions of the present invention can be combined. These modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention. All technical contents not described in detail in the present invention are well-known technologies.

Claims

1. A non-Newtonian fluid heat measurement model, characterized in that: It includes an upper frame part (3), an intermediate frame part (2) and a lower frame part (1) arranged from top to bottom. A heating chamber (4) with a detection cavity (11) is provided in the intermediate body part (2); A measuring main body (12) is provided in the inner cavity of the detection chamber (11); The measuring main component (12) includes a cylinder that is fixed or raised; A heater and a lifting cylinder (5) are respectively provided in the lower frame part (1); The inner rotor head (103) is rotated within the cylinder; The inner rotor head (103) is connected to a torque sensor and a speed sensor; A rotating inner rotor head (103) is provided inside the cylinder; The fluid to be measured is stored in a cylinder; The heating chamber (4) has a sealed baffle door (6); the lower end of the baffle door (6) is connected to the lifting cylinder (5); The heating chamber (4) is sealed and explosion-proof; The heater is connected to the heating chamber (4); The side wall of the heating box (4) is provided with a double layer; A top cavity (8) is provided at the top of the upper frame part (3); a rotary motor part (9) is provided in the top cavity (8); The rotating motor unit (9) is connected to the inner rotor head (103) via the coupling unit (10). A camera is installed in the top inner cavity (8); A side-heated snake path (14) is provided in the interlayer; An external circulation channel (15) and a venting disc (16) are provided in the heating chamber (4). An air guide (7) is provided above the top of the heating box (4); The air guide section (7) has a top inner cavity (8) at its output end; The inner rotor head (103) is equipped with an upper support body (101); an upper cross frame (102) is provided on the upper support body (101), and the inner rotor head (103) is provided on the upper cross frame (102); A carrier section (104) is provided below the inner rotor head (103); The carrier part (104) includes an electric cylinder fixing base plate (113); A servo electric cylinder (120) is installed on the electric cylinder fixing base plate (113); The upper end of the servo electric cylinder (120) is connected to a rotor fixing block (108) via an electric cylinder connecting flange (115). A force sensor is installed between the electric cylinder connecting flange (115) and the rotor fixing block (108); the servo electric cylinder (120) is equipped with a displacement sensor; A heat insulation plate (127) for the electric cylinder flange is provided between the electric cylinder connecting flange (115) and the rotor fixing block (108). A cylindrical guide frame (116) is connected to the rotor fixing block (108); a guide copper sleeve (121) is provided on the cylindrical guide frame (116). The guide copper sleeve (121) is raised and lowered on the column of the upper support body (101); A fixing block receiving cavity (109) is provided in the rotor fixing block (108), and a cylindrical heat insulation sleeve (117) is provided in the fixing block receiving cavity (109). The cylinder is installed in the cylindrical heat insulation sleeve (117); The cylinder is connected to the rotor fixing block (108) by a manual locking screw (124); The cylinder includes a lower cylinder half (111) sealed at the lower end; an upper cylinder half (110) is provided at the upper end of the lower cylinder half (111). The rotor fixing block (108) has a positive notch (130) on one side that communicates with the fixing block receiving cavity (109). A lower rotor fixing block (112) is provided in the positive notch (130); A fixing block cover plate (114) is connected to the lower rotor fixing block (112) by a pin bolt (118) and a manual locking nut (125). A heating pipe insulation sleeve (119) is provided on the electric cylinder fixing base plate (113); Side openings (129) communicating with the fixing block receiving cavity (109) are provided on both sides of the rotor fixing block (108). An air duct (128) communicating with the side opening (129) is provided on the cylinder guide frame (116); a temperature sensor (122) with a spring body (126) is provided on the lower rotor fixing block (112). Measuring holes are distributed on the cylinder; The temperature sensor (122) is used to insert into the measuring hole and contact the cylinder; The lower end of the air duct (128) is connected to a guide pipe (123) that passes through the heat insulation sleeve (119) of the heating pipe.

2. A method for measuring and calculating the heat of a non-Newtonian fluid, characterized in that: Using the model described in claim 1; The sample to be tested is filled between the cylinder and the inner rotor head (103); First, determine the parameter information; The radius of the inner rotor head (103) is The radius of the cylinder is The inner rotor head (103) has an angular velocity Rotate the cylinder and adopt a Cartesian coordinate system, aligning the z-axis with the cylinder's rotation axis, to obtain: （6）； Its boundary conditions are: ； Substituting the boundary conditions into formula (6), the fluid radius is obtained as follows: Tangential velocity at the point for: ； The velocity gradient is: ； According to the definition of a generalized Newtonian fluid, the distribution of shear stress... It can be represented as ； The torque required for the inner rotor head to rotate is ； In the formula The height of the liquid immersed in the cylinder is given by the following viscosity expression: ； Let the motor torque be M. 电 The torque M from the motor part (9) to the inner rotor head to the rotor is... 转 If e is reduced, the motor torque will be: ； Set parameters, gap, shear stress Range, unit: Pa; Rotational speed n, kR, R, k angular velocity ; Set the parameters and substitute them into formula (13); ； ； ； Viscosity ; Viscosity , Pa / s .

3. The method for measuring and calculating the heat of non-Newtonian fluids according to claim 1; characterized in that: Substitute the rotor height into formula (14); Obtain torque ; Based on the formula: shear rate = shear stress / viscosity; Shear rate, in seconds -1 Then, after determining the rotor size, the heat is calculated based on the configuration of the inner rotor head (103) and the weight of the material; The heat of the flowing material is obtained using the classic heat-temperature calculation formula; ； Represents heat, unit: J; Specific heat capacity, unit: J / (kg·K); The mass of the material flow, rotor, and cylinder; These represent the temperature changes of the material flow, rotor, and cylinder. During the shear test, the heat generated by the material temperature rise is calculated from three factors: the cylinder, the rotor, and the material itself, as shown in the following formula. ； Secondly, during the material flow test, the material is divided into four zones from bottom to top. The first zone at the bottom includes the bottom of the contact cylinder, and the fourth zone corresponds to the pressure build-up area. Temperature changes are extracted using sensors in zones one through four. With a shear gap set to 2mm, 15g of flow material fills the shear gap but not the pressure-building area. ； Similarly, calculate the heat of the material flow and the rotor in the corresponding sensor areas: ； , , These are the specific heat capacities of the cylinder, the inner rotor head, and the flowing material, respectively. , , These represent the densities of the cylinder, rotor, and flow material, respectively. , , These represent the volumes of the cylinder, rotor, and material flow within the first region, respectively. The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature obtained by the sensor in the first region. The mass of the material in the first region is calculated by volume × density, and the specific heat capacity of the material is a function of temperature, which is obtained through experiments. ； = Calculate the heat in each of the four regions: ； = , , , These are the specific heat capacities of the cylinder, rotor, and flow material, respectively. , , These represent the densities of the cylinder, rotor, and flow material, respectively. , , These represent the volumes of the cylinder, rotor, and material flow within the second region, respectively. The difference between the initial problem before the experiment and the highest temperature during the experiment is measured by the sensor in the second region; ； = ； , , These are the specific heat capacities of the cylinder, rotor, and flow material, respectively. , , These represent the densities of the cylinder, rotor, and flow material, respectively. , , These represent the volumes of the cylinder, rotor, and material flow within the third region, respectively. The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature obtained by the sensor in the third region. ； = ； , , These are the specific heat capacities of the cylinder, rotor, and flow material, respectively. , , These represent the densities of the cylinder, rotor, and flow material, respectively. , , These represent the volumes of the cylinder, rotor, and material flow within the fourth region, respectively. The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature measured by the sensor in the fourth region. The total heat is the sum of the heat from the four zones: ； ； , , These are the specific heat capacities of the cylinder, rotor, and flow material, respectively. , , These represent the densities of the cylinder, rotor, and flow material, respectively. , , These represent the volumes of the cylinder, rotor, and material flow within the first region, respectively. The difference between the initial problem before the experiment and the highest temperature during the experiment is the temperature measured by the sensor in the first region.

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