CN210774451U - Device for dynamically measuring real-time stress of motor - Google Patents
Device for dynamically measuring real-time stress of motor Download PDFInfo
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- CN210774451U CN210774451U CN201921684677.6U CN201921684677U CN210774451U CN 210774451 U CN210774451 U CN 210774451U CN 201921684677 U CN201921684677 U CN 201921684677U CN 210774451 U CN210774451 U CN 210774451U
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Abstract
The utility model relates to a device of real-time stress of dynamic measurement motor, including the atress strain cylinder, the atress strain cylinder include barrel, fixed plate and flange board, the barrel constitute by the first barrel that links to each other with the fixed plate and the second barrel that links to each other with the flange board, fixed plate, first barrel, second barrel and flange board structure as an organic whole, and whole form the top and seal, the open tubular cavity structure in bottom, be equipped with shear force foil gage and axial pressure foil gage on the inner wall of first barrel, be equipped with pressure contrast foil gage and axial pressure temperature compensation foil gage on the inner wall of second barrel. According to the above technical scheme, the utility model discloses a set up shear force foil gage, axial pressure foil gage, pressure contrast foil gage and axial pressure temperature compensation foil gage on the inner wall of stress strain cylinder respectively, axial pressure and output torque that can real-time dynamic measurement motor receive, and the measuring degree of accuracy is higher, and the function is more comprehensive.
Description
Technical Field
The utility model relates to a device of real-time stress of dynamic measurement motor.
Background
At present, common methods for measuring the torque of the motor can be divided into a transmission method and an energy conversion method. The transmission method is to calculate the torque of the motor by monitoring the change of physical parameters of the elastic element of the transmission torque; the energy conversion method is to indirectly measure torque by measuring other parameters such as heat energy and electric energy according to the law of conservation of energy. The existing energy conversion method can be used for finished equipment, but has the defects of large volume, high requirement on working environment and the like, and is limited in application. The transmission method can be designed into measuring devices with various shapes and volumes by means of elastic elements, and has strong adaptability, high precision and most extensive application.
In the category of a transmission method, the related domestic motor force measurement method only measures torque, and no method or equipment for simultaneously measuring torque and axial force is available. Axial force measurements are found on many devices, such as the drilling machinery, vehicle, construction, etc., where the axial force of a rod or shaft is monitored. Monitoring equipment based on a transmission method cannot simultaneously measure the torque and the axial pressure. In addition, the existing measuring device directly pastes the stress sheet on the outer surface of the columnar measured component, and during working, the measuring device and the stress sheet are easily scratched to cause damage, influence on the measuring precision or fail.
SUMMERY OF THE UTILITY MODEL
The utility model aims to provide a device for dynamically measuring the real-time stress of a motor, which can simultaneously measure the axial compressive stress and the circumferential shear stress of the motor, thereby obtaining the axial force and the torque; simultaneously, the strain gauge of the device is arranged inside the steel structure, and the device is stable in performance and not easy to damage.
In order to achieve the above purpose, the utility model adopts the following technical scheme: the stress strain cylinder comprises a cylinder body, a fixing plate fixed at the top end of the cylinder body and a flange plate fixed at the bottom end of the cylinder body, wherein the cylinder body consists of a first cylinder body connected with the fixing plate and a second cylinder body connected with the flange plate, the fixing plate, the first cylinder body, the second cylinder body and the flange plate are of an integrated structure and integrally form a cylindrical cavity structure with a closed top end and an open bottom end, the inner diameters of the first cylinder body and the second cylinder body are equal, the outer diameter of the first cylinder body is smaller than that of the second cylinder body, the diameter of the fixing plate is matched with that of the first cylinder body, the inner wall of the first cylinder body is provided with shear strain gauges and axial pressure strain gauges, the shear strain gauges and the axial pressure strain gauges are uniformly arranged at intervals along the inner wall of the first cylinder body and are at the same height, the inner wall of the second cylinder body is provided with pressure contrast strain gauges and axial pressure temperature compensation strain gauges, the pressure contrast strain gauges and the axial pressure temperature compensation strain gauges are uniformly arranged at intervals along the inner wall of the second cylinder body and are located at the same height, the pressure contrast strain gauges and the axial pressure temperature compensation strain gauges are respectively located under the shear strain gauges and the axial pressure strain gauges, the shear strain gauges, the axial pressure strain gauges, the pressure contrast strain gauges and the axial pressure temperature compensation strain gauges are respectively arranged in two groups, each group of shear strain gauges is provided with two shear strain gauges, and each group of axial pressure strain gauges, pressure contrast strain gauges and axial pressure temperature compensation strain gauges is respectively provided with one strain gauge.
The two groups of shear strain gauges and the two groups of axial pressure strain gauges are both located at the middle height of the inner wall of the first cylinder body, the two shear strain gauges in each group are arranged in a mirror image mode along the horizontal line, included angles between the two shear strain gauges in each group and the horizontal line are +/-45 degrees, and intersection points of the two shear strain gauges in each group and the horizontal line are overlapped.
The two groups of pressure contrast strain gauges and the two groups of axial pressure temperature compensation strain gauges are both positioned at the middle height of the inner wall of the second cylinder body.
Shear force foil gage, axial pressure foil gage, pressure contrast foil gage and axial pressure temperature compensation foil gage be foil resistance foil gage, wherein: the setting direction of the resistance wire in the axial pressure temperature compensation strain gauge is perpendicular to the axis of the stress strain cylinder, and the setting directions of the resistance wire in the pressure contrast strain gauge and the axial pressure strain gauge are parallel to the axis of the stress strain cylinder.
The wall thickness ratio of the first cylinder to the second cylinder is less than 1: 2, the ratio of the cross section of the second cylinder to the cross section of the first cylinder is greater than 2.5: 1.
the fixed plate is connected with the motor fixing base through screws, screw holes connected with the motor fixing base are formed in the fixed plate, the outer diameter of the flange plate is larger than that of the second cylinder, the inner diameter of the flange plate is smaller than that of the second cylinder, and the flange plate is connected with the motor stator in a welded mode.
The stress strain cylinder is a steel strain cylinder.
According to the above technical scheme, the utility model discloses a set up shear force foil gage, axial pressure foil gage, pressure contrast foil gage and axial pressure temperature compensation foil gage on the inner wall of stress strain cylinder respectively, axial pressure and output torque that can real-time dynamic measurement motor receive, and the measuring degree of accuracy is higher, and the function is more comprehensive.
Drawings
Fig. 1 is a schematic structural diagram of the present invention;
FIG. 2 is a cross-sectional view A-A of FIG. 1;
FIG. 3 is a diagram illustrating the usage status of the present invention;
FIG. 4 is a schematic circuit diagram of the torque measurement of the present invention;
fig. 5 is a schematic circuit diagram of the axial force comparison measurement of the present invention.
Detailed Description
The present invention will be further explained with reference to the accompanying drawings:
the device for dynamically measuring the real-time stress of the motor as shown in fig. 1, fig. 2 and fig. 3 comprises a stress-strain cylinder arranged between the motor and a motor fixing base, preferably, the stress-strain cylinder is a steel strain cylinder which can be made of 45# steel. The stress strain cylinder comprises a cylinder body 1, a fixing plate 2 fixed on the top end of the cylinder body 1 and a flange plate 3 fixed at the bottom end of the cylinder body 1, wherein the cylinder body 1 is composed of a first cylinder body 11 connected with the fixing plate 2 and a second cylinder body 12 connected with the flange plate 3, the fixing plate 2, the first cylinder body 11, the second cylinder body 12 and the flange plate 3 are of an integrated structure, the integrated structure is a cylindrical cavity structure with a closed top end and an open bottom end, the inner diameters of the first cylinder body 11 and the second cylinder body 12 are equal, the outer diameter of the first cylinder body 11 is smaller than that of the second cylinder body 12, and the diameter of the fixing plate 2 is identical to that of the first cylinder body 11. Specifically speaking, whole atress strain cylinder is the cavity structure, and inside diameter is even, and the variable cross section design is adopted to the outside, includes the four sections altogether: fixing plate 2 forms structure stiff end A promptly, and first barrel 11 forms strain measurement section B, and second barrel 12 forms temperature compensation section C, and flange plate 3 forms motor linkage segment D, also is the connection structure that whole atress meets an emergency a section of thick bamboo adoption four-section formula, and its advantage lies in: 1) the compressive stiffness of the strain measurement section B is less than 40% of that of the temperature compensation section C, and a strain amount which can be monitored is easily generated; the deformation of the temperature compensation section C is small, and the temperature compensation section C is more stable as a carrier of a temperature compensation sheet; 2) the multifunctional axial strain monitoring device has the advantages that multiple functions are realized by adopting a simple structure, and axial strain, shear strain, temperature compensation and axial strain comparison can be monitored; 3) the structure is compact, the processing is convenient, and the design can be adjusted according to the size and the use space of the motor; 4) the temperature compensation section C is located immediately adjacent to the strain measurement section B to minimize the effect of temperature differences.
Further, the inner wall of the first cylinder 11 is provided with shear strain gauges 4 and axial pressure strain gauges 5, the shear strain gauges 4 and the axial pressure strain gauges 5 are uniformly arranged at intervals along the inner wall of the first cylinder 11 and are located at the same height, the inner wall of the second cylinder 12 is provided with pressure comparison strain gauges 6 and axial pressure temperature compensation strain gauges 7, the pressure comparison strain gauges 6 and the axial pressure temperature compensation strain gauges 7 are uniformly arranged at intervals along the inner wall of the second cylinder 12 and are located at the same height, the pressure comparison strain gauges 6 and the axial pressure temperature compensation strain gauges 7 are respectively located right below the shear strain gauges 4 and the axial pressure strain gauges 5, two groups of the shear strain gauges 4, two groups of the axial pressure strain gauges 5, two groups of the pressure comparison strain gauges 6 and two groups of the axial pressure temperature compensation strain gauges 7 are respectively arranged, two shear strain gauges 4 are arranged, and the axial pressure strain gauges 5, two groups of the axial pressure strain gauges 5 and the axial pressure, The pressure contrast strain gauges 6 and the axial pressure temperature compensation strain gauges 7 are respectively arranged one by one, namely four shear strain gauges 4, two axial pressure strain gauges 5, two pressure contrast strain gauges 6 and two axial pressure temperature compensation strain gauges 7 are arranged in total, two groups of shear strain gauges 4 are symmetrically arranged at intervals of 180 degrees, two groups of axial pressure strain gauges 5 are symmetrically arranged at intervals of 180 degrees and are 90 degrees apart from the shear strain gauges 4; two sets of pressure contrast foil gauges 6 interval 180 degrees symmetry sets up, and two sets of axial pressure temperature compensation foil gauges 7 interval 180 degrees symmetry sets up, and with the pressure contrast foil gauge 6 interval 90 degrees. The pressure comparison strain gauge 6 is used for detecting the axial strain of the temperature compensation section C of the strain pressure cylinder, comparing the axial strain with the strain value of the strain measurement section B, and testing the reliability of axial stress measurement.
The connection relationship among the strain gauges is as follows:
firstly, measuring the axial force.
The two sets of axial pressure strain gauges 5 and the two sets of axial pressure temperature compensation strain gauges 7 form a full-bridge circuit, and the axial pressure strain gauges 5 and the axial pressure temperature compensation strain gauges 7 are connected at intervals and connected with a measuring instrument.
And II, measuring the torque.
The two groups of shear strain gauges 4 form a full-bridge circuit, and the strain gauges in the same group are adjacently connected and connected to a measuring instrument.
The full bridge circuit schematic is shown in fig. 4, wherein: e is the bridge voltage, E0Is the output voltage; when measuring compressive strain, the axial pressure temperature compensation strain gauge is arranged in Rg2And Rg4A location; when measuring shear strain, Rg1、Rg2Are in a group, Rg3、Rg4Are grouped.
And thirdly, comparing and measuring the axial force. Two groups of pressure comparison strain gauges 6 are connected into a full-bridge circuit by means of two equivalent fixed resistors R and are connected with a measuring instrument.
The electrical schematic of the axial force comparison measurement is shown in fig. 5, in which: e is the bridge voltage, E0Is the output voltage; the strain gauge is arranged at Rg1And Rg2Location.
Further, the wall thickness ratio of the first cylinder 11 to the second cylinder 12 is less than 1: 2, the ratio of the cross section of the second cylinder 12 to the first cylinder 11 is greater than 2.5: 1, the temperature compensation section C has much smaller strain than the strain measurement section B, and the axial pressure temperature compensation strain gauge is arranged according to the direction of eliminating the strain influence, so the axial pressure temperature compensation strain gauge is reliably applicable.
Further, two sets of shear strain gages 4 and two sets of axial compression strain gages 5 are all located the middle height of first barrel 11 inner wall, and two shear strain gages 4 in each group set up along the water flat line mirror image and be ± 45 with the contained angle of water flat line respectively, and two shear strain gages 4 in each group coincide with the nodical of water flat line. The arrangement mode can eliminate the temperature influence of the lead, eliminate the integral bending strain and the compressive and tensile strain, and finally calculate the magnitude of the received torsional force by calibrating the elastic modulus.
Furthermore, two sets of pressure contrast foil gages 6 and two sets of axial pressure temperature compensation foil gages 7 are located at the middle height of the inner wall of the second cylinder.
Further, shear strain gauge 4, axial pressure strain gauge 5, pressure contrast strain gauge 6 and axial pressure temperature compensation strain gauge 7 are foil resistance strain gauges, wherein: the arrangement direction of the resistance wire in the axial pressure temperature compensation strain gauge 7 is vertical to the axis of the stress strain cylinder, and the arrangement directions of the resistance wire in the pressure contrast strain gauge 6 and the resistance wire in the axial pressure strain gauge 5 are parallel to the axis of the stress strain cylinder.
The fixing plate 2 is connected with the motor fixing base through screws, a screw hole 21 connected with the motor fixing base is formed in the fixing plate 2, the outer diameter of the flange plate 3 is larger than the outer diameter of the second cylinder 12, the inner diameter of the flange plate 3 is smaller than the inner diameter of the second cylinder 12, and the flange plate 3 is connected with the motor stator 100 in a welding mode.
The following description of the working principle is made by the typical connection of the present invention:
when the device is used, the motor is connected to the support or the base through the device, the output shaft of the motor and the connecting piece are connected with the reduction gearbox, and the reduction gearbox is connected with the drill rod through the clamp.
Firstly, axial pressure or tension borne by the drill rod is transmitted to a stress strain cylinder through a reduction gearbox and a motor, the stress strain cylinder generates compression or tensile strain, and then the axial pressure or tension magnitude is calculated. The resistance wire of the axial pressure temperature compensation strain gauge is perpendicular to the stress axis direction, and the deformation of the temperature compensation section is smaller than that of the strain measurement section, so that the strain of the temperature compensation strain gauge is considered to be 0.
In a full bridge circuit, the bridge voltage E, the output voltage E0The strain calculation formula is as follows:
ε0＝2e0/(EKs)；
wherein: ksIs the strain rate of the strain gage.
The overall compression force calculation formula is as follows:
N＝ε0EtA；
wherein: n is pressure, EtThe elastic modulus of the strain cylinder material is A, and the sectional area of the strain cylinder is A.
And II, comparing the axial pressure.
Similarly, the parameters are obtained by adopting a full-bridge circuit, and the calculation formula is the same as above. Except that the sectional area (A) of the strain cylinder adopts the sectional area of the temperature compensation section. And checking the accuracy of the axial stress of the strain measurement section through the pressure comparison value.
And thirdly, calculating the torque force. When the drill rod works, the torque output by the motor is different when the drill rod meets various friction or resistance. And calculating the magnitude of the output torque force by combining the strain amount of the shear strain gauge with the torsional rigidity of the strain cylinder detected and calibrated in advance.
In a full bridge circuit, the bridge voltage E, the output voltage E0The shear strain calculation formula is:
ε0＝e0/(EKs)；
wherein: ksIs the strain rate of the strain gage.
The overall torque force calculation formula is as follows:
T＝ε0GIp＝ε0Kg；
wherein: t is torsion, G is shear modulus of strain cylinder material, IpIs the polar inertia moment of the cross section of the strain cylinder, KgAnd calibrating the torsional rigidity coefficient for detection.
Example (b):
the stress strain cylinder of the utility model adopts No. 45 steel with a height of 50mm, wherein the strain measurement section B has a height of 27mm and an outer diameter of 50 mm; the height of the temperature compensation section C is 12mm, and the outer diameter is 60 mm; the inner diameter of a cylindrical cavity enclosed by the fixing plate 2, the first cylinder 11, the second cylinder 12 and the flange plate 3 is 42mm, and the height is 39 mm. And installing four resistance strain gauges according to the arrangement mode, and carrying out pressure and torsion calibration on the pressure strain cylinder to obtain a compression stiffness coefficient and a torsional stiffness coefficient. All the strain gauges have the same parameters, and the specific parameters are as follows:
strain gauge area 3 × 5mm, measurement structure material constantan, carrier material polyimide, thickness 45 μm, nominal resistance 120, working temperature range-10 to 115 deg.C, temperature coefficient (115 + -10) × 10-6and/K, the minimum bending curvature radius at the reference temperature is 10mm, and the mechanical hysteresis is 0.5-1 μm/m.
The equipment is arranged on a small-sized drilling machine bracket, a motor, a columnar planet wheel reduction box and a drill rod clamp are arranged, a resistance strain gauge is connected to a data acquisition unit, and the data acquisition unit is connected with a programmed singlechip through a data line. The motor and the instrument are powered by an 18V lithium iron phosphate battery. Drilling tests are carried out on suburb soil layers by using the drilling machine, the drilling depth is 3.5m, the soil layer with the upper part of 1.5m has the torque of 2-5 N.m, the pressure of 19-35N and the axial contrast pressure of 20-37N; the soil layer with the lower 2.5m has the torque of 5-20 N.m, the pressure of 30-80N and the axial contrast pressure of 31-79N. The method is very close to the measurement data of other external torsion meters and pressure meters on a single drill pipe. Meanwhile, the axial contrast pressure of the device is slightly different from the main pressure, and the maximum difference is about 5%. The above situation illustrates that the compressive stress measurement is accurate and reliable. And then, trial drilling is continuously carried out near the drilled hole, displayed data are stable, the similarity is strong, and the difference with independent measurement data of other external torsionmeters and pressure gauges is 3-5%.
To sum up, the utility model discloses a dynamic measurement motor real-time stress device has good stability and adaptability, can be accurate, the strain value of real-time measurement strain cylinder, and real-time calculation shows axial pressure (pulling force) and torsion that the motor receives.
The beneficial effects of the utility model reside in that: 1) the utility model can dynamically measure the axial pressure and output torque force of the motor in real time; 2) the utility model is respectively provided with the shear strain gauge, the axial pressure strain gauge, the pressure contrast strain gauge and the axial pressure temperature compensation strain gauge, the measuring accuracy is higher, and the function is more comprehensive; 3) the arrangement mode of the shear strain gauge and the axial pressure strain gauge of the utility model can accurately measure the shear strain and the axial pressure strain, thereby obtaining the torque force and the axial pressure of the motor; 4) the utility model has compact appearance and reasonable structure.
The above-mentioned embodiments are only for describing the preferred embodiments of the present invention, and are not intended to limit the scope of the present invention, and various modifications and improvements made by those skilled in the art without departing from the design spirit of the present invention should fall into the protection scope defined by the claims of the present invention.
Claims (7)
1. The utility model provides a device of real-time stress of dynamic measurement motor which characterized in that: the stress strain cylinder comprises a stress strain cylinder arranged between a motor and a motor fixing base, wherein the stress strain cylinder comprises a cylinder body (1), a fixing plate (2) fixed at the top end of the cylinder body (1) and a flange plate (3) fixed at the bottom end of the cylinder body (1), the cylinder body (1) is composed of a first cylinder body (11) connected with the fixing plate (2) and a second cylinder body (12) connected with the flange plate (3), the fixing plate (2), the first cylinder body (11), the second cylinder body (12) and the flange plate (3) are of an integrated structure and integrally form a cylindrical cavity structure with a closed top end and an open bottom end, the inner diameters of the first cylinder body (11) and the second cylinder body (12) are equal, the outer diameter of the first cylinder body (11) is smaller than the outer diameter of the second cylinder body (12), and the diameter of the fixing plate (2) is matched with the outer diameter of the first cylinder body (11), the shear strain gauge comprises a first cylinder (11), wherein shear strain gauges (4) and axial pressure strain gauges (5) are arranged on the inner wall of the first cylinder (11), the shear strain gauges (4) and the axial pressure strain gauges (5) are uniformly arranged at intervals along the inner wall of the first cylinder (11) and are located at the same height, pressure comparison strain gauges (6) and axial pressure temperature compensation strain gauges (7) are arranged on the inner wall of a second cylinder (12), the pressure comparison strain gauges (6) and the axial pressure temperature compensation strain gauges (7) are uniformly arranged at intervals along the inner wall of the second cylinder (12) and are located at the same height, the pressure comparison strain gauges (6) and the axial pressure temperature compensation strain gauges (7) are respectively located under the shear strain gauges (4) and the axial pressure strain gauges (5), and the shear strain gauges (4), the axial pressure strain gauges (5) and the axial pressure strain gauges (5) are arranged on the inner wall of the first cylinder (11), and the shear strain gauges (4), the axial pressure, The pressure contrast strain gauge (6) and the axial pressure temperature compensation strain gauge (7) are respectively provided with two groups, each group of shear strain gauges (4) is provided with two shear strain gauges, and the axial pressure strain gauge (5), the pressure contrast strain gauge (6) and the axial pressure temperature compensation strain gauge (7) in each group are respectively provided with one shear strain gauge.
2. The device for dynamically measuring the real-time stress of the motor according to claim 1, wherein: the two groups of shear strain gauges (4) and the two groups of axial pressure strain gauges (5) are both located at the middle height of the inner wall of the first cylinder body (11), the two shear strain gauges (4) in each group are arranged in a mirror image mode along the horizontal line, included angles between the two shear strain gauges (4) in each group and the horizontal line are +/-45 degrees respectively, and intersection points of the two shear strain gauges (4) in each group and the horizontal line are overlapped.
3. The device for dynamically measuring the real-time stress of the motor according to claim 1, wherein: the two groups of pressure contrast strain gauges (6) and the two groups of axial pressure temperature compensation strain gauges (7) are both positioned at the middle height of the inner wall of the second cylinder.
4. The device for dynamically measuring the real-time stress of the motor according to claim 1, wherein: shear strain gauge (4), axial pressure foil gauge (5), pressure contrast foil gauge (6) and axial pressure temperature compensation foil gauge (7) be foil resistance strain gauge, wherein: the arrangement direction of the resistance wire in the axial pressure temperature compensation strain gauge (7) is vertical to the axis of the stress strain cylinder, and the arrangement directions of the resistance wire in the pressure contrast strain gauge (6) and the axial pressure strain gauge (5) are parallel to the axis of the stress strain cylinder.
5. The device for dynamically measuring the real-time stress of the motor according to claim 1, wherein: the wall thickness ratio of the first cylinder (11) to the second cylinder (12) is less than 1: 2, the ratio of the cross section of the second cylinder (12) to the cross section of the first cylinder (11) being greater than 2.5: 1.
6. the device for dynamically measuring the real-time stress of the motor according to claim 1, wherein: fixed plate (2) pass through the screw connection with motor unable adjustment base, fixed plate (2) on be equipped with screw (21) that link to each other with motor unable adjustment base, the external diameter of flange board (3) is greater than the external diameter of second barrel (12), the internal diameter of flange board (3) is less than the internal diameter of second barrel (12), flange board (3) link to each other with motor stator (100) welding.
7. The device for dynamically measuring the real-time stress of the motor according to claim 1, wherein: the stress strain cylinder is a steel strain cylinder.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201921684677.6U CN210774451U (en) | 2019-10-09 | 2019-10-09 | Device for dynamically measuring real-time stress of motor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201921684677.6U CN210774451U (en) | 2019-10-09 | 2019-10-09 | Device for dynamically measuring real-time stress of motor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114952693A (en) * | 2021-02-26 | 2022-08-30 | 硕丰工业股份有限公司 | Clutch type power transmission device and torsion detection module thereof |
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2019
- 2019-10-09 CN CN201921684677.6U patent/CN210774451U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114952693A (en) * | 2021-02-26 | 2022-08-30 | 硕丰工业股份有限公司 | Clutch type power transmission device and torsion detection module thereof |
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